CN113167275A - Screw compressor - Google Patents

Screw compressor Download PDF

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Publication number
CN113167275A
CN113167275A CN201980079092.8A CN201980079092A CN113167275A CN 113167275 A CN113167275 A CN 113167275A CN 201980079092 A CN201980079092 A CN 201980079092A CN 113167275 A CN113167275 A CN 113167275A
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CN
China
Prior art keywords
rotor
flow path
female
male
suction
Prior art date
Legal status (The legal status 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 status listed.)
Pending
Application number
CN201980079092.8A
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Chinese (zh)
Inventor
千叶纮太郎
高野正彦
頼金茂幸
森田谦次
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Industrial Equipment Systems Co Ltd
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Hitachi Industrial Equipment Systems Co Ltd
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
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Publication of CN113167275A publication Critical patent/CN113167275A/en
Pending legal-status Critical Current

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08Rotary-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
    • F04C18/12Rotary-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
    • F04C18/14Rotary-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
    • F04C18/16Rotary-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/20Rotors
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/30Casings or housings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00Geometry
    • F04C2250/10Geometry of the inlet or outlet
    • F04C2250/101Geometry of the inlet or outlet of the inlet

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

Abstract

The invention provides a screw compressor capable of reducing pressure loss of a suction flow path. A casing (12) of a screw compressor comprises: a cylinder chamber (21) which houses the tooth (13A) of the male rotor (11A) and the tooth (13B) of the female rotor (11B) and forms a working chamber in the tooth grooves thereof; a suction port (22) located on the outer side in the radial direction of the rotor; and an intake flow path (23) that communicates with the working chamber in the intake stroke in the axial direction of the rotor. The suction flow path (23) has a male rotor side suction flow path (26A) located on the male rotor (11A) side and located on the downstream side of the virtual plane (C), and a female rotor side suction flow path (26B) located on the female rotor (11B) side and located on the downstream side of the virtual plane (C). The male rotor side intake flow path (26A) is formed in such a manner that the flow path wall (27A) on the outer side in the rotor radial direction is at the same position as the wall of the cylinder chamber (21) when viewed in the rotor axial direction, at least in the range from the intake side end face of the tooth (13A) of the male rotor (11A) in the rotor axial direction to half the axial pitch (P1) of the tooth (13A).

Description

Screw compressor
Technical Field
The present invention relates to a screw compressor having a suction port located radially outside a rotor and a suction flow path communicating with a working chamber in an axial direction of the rotor.
Background
The screw compressor described in patent document 1 includes a male rotor having a tooth portion, a female rotor having a tooth portion meshing with the tooth portion of the male rotor, and a casing housing the male rotor and the female rotor.
The housing has a cylinder chamber that houses the teeth of the male rotor and the teeth of the female rotor, and forms a working chamber on the male rotor side and a working chamber on the female rotor side in their tooth grooves. The housing has a suction port located on the outer side of the teeth of the male rotor and the teeth of the female rotor in the rotor radial direction, and a suction flow path formed to connect the suction port and a working chamber of a suction stroke. The housing has a discharge port located on the outer side of the teeth of the male rotor and the teeth of the female rotor in the rotor radial direction, and a discharge flow path formed so as to connect the discharge port and a working chamber of a discharge stroke.
The working chamber changes its volume as it moves from one side to the other side in the axial direction of the rotor. Thus, the working chamber sequentially performs an intake stroke for taking in gas from the intake port via the intake flow path, a compression stroke for compressing the gas, and a discharge stroke for discharging the compressed gas to the discharge port via the discharge flow path.
The suction flow path communicates with the working chamber in the suction stroke in the rotor axial direction. The suction flow path includes a male rotor-side suction flow path on the male rotor side and on the downstream side of a virtual plane passing through the central axis of the male rotor and the central axis of the female rotor (in other words, on the opposite side of the suction port), and a female rotor-side suction flow path on the female rotor side and on the downstream side of the virtual plane.
Documents of the prior art
Patent document
Patent document 1: japanese patent laid-open No. 2012 and 041910 (see, for example, FIGS. 8 and 9)
Disclosure of Invention
Problems to be solved by the invention
In patent document 1, a flow path wall on the outer side in the rotor radial direction of the male rotor side suction flow path (except for a portion for enclosing gas in the working chamber) is located on the outer side in the rotor radial direction than a wall of the cylinder chamber. Therefore, a component in the rotor radial direction is generated as a component of the air flow flowing from the male rotor side suction flow path to the male rotor side working chamber, and this becomes a significant cause of an increase in pressure loss.
Similarly, the flow path wall on the outer side in the rotor radial direction of the female rotor-side intake flow path (excluding the wall portion for enclosing gas in the working chamber) is located on the outer side in the rotor radial direction than the wall of the cylinder chamber. Therefore, a component in the rotor radial direction is generated as a component of the air flow flowing from the suction flow passage on the female rotor side to the working chamber on the female rotor side, and this causes an increase in pressure loss.
The present invention has been made in view of the above circumstances, and an object thereof is to reduce a pressure loss in a suction flow path.
Means for solving the problems
In order to solve the above problem, the configurations described in the scope of the claims are applied. The present invention includes a plurality of the above-described means for solving the problem, and an example thereof is a screw compressor including: a male rotor having a tooth; a female rotor having a tooth portion meshing with the tooth portion of the male rotor; and a housing that houses the male rotor and the female rotor, the housing including: a cylinder chamber for housing the tooth portions of the male rotor and the tooth portions of the female rotor and forming a working chamber on the male rotor side and a working chamber on the female rotor side in their tooth grooves; a suction port located on the outer side of the tooth part of the male rotor and the tooth part of the female rotor in the radial direction of the rotor; and an intake flow path formed to connect the intake port and a working chamber of an intake stroke and communicating with the working chamber of the intake stroke in a rotor axial direction, the intake flow path including: a male rotor side suction flow path which is located on the male rotor side and is located on a downstream side of an imaginary plane passing through a central axis of the male rotor and a central axis of the female rotor; and a female rotor side suction flow path located on the female rotor side and located on a downstream side of the virtual plane, wherein: the male rotor side suction flow path is formed as follows: the flow path wall on the outer side in the rotor radial direction is located at the same position as the wall of the cylinder chamber when viewed in the rotor axial direction, at least in a range from the suction-side end surface of the teeth of the male rotor in the rotor axial direction to half of the pitch in the axial direction of the teeth.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the present invention, the pressure loss in the suction flow path can be reduced.
The problems, structures, and effects other than those described above will be apparent from the following description.
Drawings
Fig. 1 is a schematic diagram showing a structure of an oil-supply type screw compressor according to an embodiment of the present invention.
Fig. 2 is a vertical sectional view showing a structure of a compressor main body according to an embodiment of the present invention.
Fig. 3 is a horizontal sectional view of section III-III of fig. 2.
Fig. 4 is a vertical sectional view of section IV-IV of fig. 2.
Fig. 5 is a vertical sectional view of section V-V of fig. 2.
Fig. 6 is a horizontal sectional view showing a structure of a compressor main body according to a modification of the present invention.
Detailed Description
An embodiment of the present invention will be described with reference to fig. 1 to 5.
The screw compressor of the present embodiment includes: a motor 1; a compressor main body 2 driven by a motor 1 and compressing air (gas); a gas-liquid separator 3 that separates compressed air discharged from the compressor main body 2 and oil (liquid) contained therein; and an oil pipe 4 for supplying the oil separated by the gas-liquid separator 3 to the compressor body 2 (specifically, a working chamber, a suction-side bearing, and a discharge-side bearing, which will be described later). The oil pipe 4 is provided with an oil cooler 5 for cooling oil, an oil filter 6 for removing impurities in the oil, and the like.
The compressor body 2 includes a male rotor 11A and a female rotor 11B as screw rotors, and a housing 12 that houses the male rotor 11A and the female rotor 11B.
The male rotor 11A includes a tooth portion 13A having a plurality of (4 in the present embodiment) teeth extending in a spiral shape, an intake side shaft portion 14A connected to one axial side (left side in fig. 2 and 3) of the tooth portion 13A, and a discharge side shaft portion 15A connected to the other axial side (right side in fig. 2 and 3) of the tooth portion 13A. The intake side shaft 14A of the male rotor 11A is rotatably supported by an intake side bearing 16A, and the discharge side shaft 15A of the male rotor 11A is rotatably supported by a discharge side bearing 17A.
Similarly, the female rotor 11B includes a tooth portion 13B having a plurality of (6 in the present embodiment) teeth extending in a spiral shape, an intake-side shaft portion 14B connected to one axial side (left side in fig. 2 and 3) of the tooth portion 13B, and a discharge-side shaft portion 15B connected to the other axial side (right side in fig. 2 and 3) of the tooth portion 13B. The suction-side shaft 14B of the female rotor 11B is rotatably supported by a suction-side bearing 16B, and the discharge-side shaft 15B of the female rotor 11B is rotatably supported by a discharge-side bearing 17B.
The suction-side shaft portion 14A of the male rotor 11A penetrates the housing 12 and is coupled to the rotating shaft of the electric motor 1. The male rotor 11A is rotated by driving of the motor 1, and the female rotor 11B is also rotated by meshing the teeth 13A of the male rotor 11A with the teeth 13B of the female rotor 11B.
The casing 12 is composed of a main casing 18, an intake-side casing 19 coupled to one axial side (left side in fig. 2 and 3) of the main casing 18, and a discharge-side casing 20 coupled to the other axial side (right side in fig. 2 and 3) of the main casing 18.
The housing 12 includes a tooth portion 13A of the male rotor 11A and a tooth portion 13B of the female rotor 11B, and cylinder chambers 21 in which a working chamber on the male rotor side and a working chamber on the female rotor side are formed in their tooth grooves. The cylinder chamber 21 is configured such that 2 cylindrical holes for respectively housing the tooth portions 13A and 13B of the male rotor 11A and the female rotor 11B partially overlap with each other (see fig. 5).
The casing 12 includes a suction port 22 located on the outer side (upper side in fig. 2) in the rotor radial direction than the teeth 13A of the male rotor 11A and the teeth 13B of the female rotor 11B, and a suction flow path 23 formed to connect the suction port 22 and a working chamber of a suction stroke. A cylinder chamber 21, a suction port 22, and a suction flow path 23 are formed in the main casing 18.
The casing 12 has a discharge port 24 located on the outer side (lower side in fig. 2) in the rotor radial direction than the teeth 13A of the male rotor 11A and the teeth 13B of the female rotor 11B, and a discharge flow path 25 formed to connect the discharge port and a working chamber of a discharge stroke. The discharge port 24 is formed in the discharge-side housing 20, and the discharge flow path 25 is formed in the discharge-side housing 20 and the main casing 18.
The working chamber changes its volume as it moves from one side to the other side in the axial direction of the rotor. Thus, the working chamber sequentially performs an intake stroke for taking in gas from the intake port 22 via the intake flow path 23, a compression stroke for compressing the gas, and a discharge stroke for discharging the compressed gas to the discharge port 24 via the discharge flow path 25.
The suction flow path 23 communicates with the working chamber in the suction stroke in the rotor axial direction. The suction flow path 23 includes a male rotor-side suction flow path 26A on the male rotor 11A side and on the downstream side of a virtual plane C passing through the central axis O1 of the male rotor 11A and the central axis O2 of the female rotor 11B (in other words, on the opposite side of the suction port 22), and a female rotor-side suction flow path 26B on the female rotor 11B side and on the downstream side of the virtual plane C (see fig. 3 and 4).
Here, as a great feature of the present embodiment, the flow path wall 27A on the outer side in the rotor radial direction of the male rotor-side intake flow path 26A (except for the portion 28 for enclosing gas in the working chamber) is formed so as to be located at the same position as the wall of the cylinder chamber 21 when viewed in the rotor axial direction in a range from at least the suction-side end surface of the teeth 13A of the male rotor 11A in the rotor axial direction to half of the axial pitch P1 (see fig. 3) of the teeth 13A (specifically, a range of P1 × 0.8 to R1 in fig. 3, and a range of P1 × 0.5 to R1 in fig. 6 described later). The axial pitch of the teeth means the interval of the tooth tips in the rotor axial direction. In addition, considering machining errors and the like, the position of the flow path wall 27A in the radial direction as viewed in the rotor axial direction is the same as the position of the wall of the cylinder chamber 21, that is, the radial direction position of the flow path wall 27A with respect to the central axis O1 of the male rotor 11A is in the range of 95% to 105% of the radial direction position of the wall of the cylinder chamber 21.
The flow path wall 27B on the rotor radial direction outer side of the female rotor-side intake flow path 26B (except for the portion 28 for enclosing gas in the working chamber) is formed so as to be located at the same position as the wall of the cylinder bore 21 when viewed in the rotor axial direction in a range (specifically, a range of P2 × 0.8 in fig. 3 and a range of P2 × 0.5 in fig. 6 to be described later) at least half of the axial pitch P2 (where P1 is P2-see fig. 3) of the teeth 13B of the male rotor 11B from the suction-side end face of the teeth 13B in the rotor axial direction to the teeth 13B. In addition, considering machining errors and the like, the flow path wall 27B is located at the same position as the wall of the cylinder chamber 21 when viewed from the rotor axial direction, and the radial position of the flow path wall 27B with respect to the central axis O2 of the female rotor 11B is in the range of 95% to 105% of the radial position of the wall of the cylinder chamber 21.
In the above embodiment, since a component in the rotor radial direction is less likely to be generated as a component of the air flow flowing from the male rotor side suction passage 26A to the male rotor side working chamber, the pressure loss can be reduced. Further, since a component in the rotor radial direction is less likely to be generated as a component of the air flow flowing from the female rotor side suction flow path 26B to the female rotor side working chamber, the pressure loss can be reduced. As a result, the intake air flow rate can be increased and the power can be reduced.
Further, as compared with the case where the flow path walls 27A, 27B are located on the outer side in the rotor radial direction than the wall of the cylinder chamber 21, oil accumulation in the lower portion of the male rotor side suction flow path 26A and the female rotor side suction flow path 26B can be suppressed when the compressor main body 2 is stopped. Therefore, it is possible to suppress pressure loss due to the influence of oil existing in the lower portion of the male rotor side intake flow passage 26A and the female rotor side intake flow passage 26B.
The flow path walls 27A and 27B are located at the same positions as the walls of the cylinder chambers 21 when viewed in the rotor axial direction, and are supplemented by the reason that the flow path walls extend at least from the suction-side end surfaces of the teeth of the rotor in the rotor axial direction to a half of the axial pitch of the teeth. From the viewpoint of the volumetric efficiency of the screw compressor, it is necessary to consider the area of the rotor axial cross section of the male rotor-side suction passage 26A with respect to the area of the rotor axial cross section of the male rotor-side working chamber (in other words, the cross section extending in the rotor axial direction) and the area of the rotor axial cross section of the female rotor-side suction passage 26B with respect to the area of the rotor axial cross section of the female rotor-side working chamber. The rotor axial cross-sectional area of the male rotor-side working chamber is expressed by, for example, (difference between the outer diameter of the teeth of the male rotor and the outer diameter of the shaft) × axial pitch ÷ 2, and therefore the rotor axial cross-sectional area of the male rotor-side suction flow passage 26A is preferably secured by at least (difference between the outer diameter of the teeth of the male rotor and the outer diameter of the shaft) × axial pitch ÷ 2. Similarly, the area of the rotor axial cross section of the female rotor-side working chamber is expressed by, for example, (difference between the outer diameter of the teeth of the female rotor and the outer diameter of the shaft) × axial pitch ÷ 2, and therefore the area of the rotor axial cross section of the female rotor-side suction flow passage 26B is preferably at least secured (difference between the outer diameter of the teeth of the female rotor and the outer diameter of the shaft) × axial pitch ÷ 2. From such a viewpoint, if the male rotor-side intake flow path 26A or the female rotor-side intake flow path 26B is characterized by not having at least the range from the suction-side end face of the teeth of the rotor to half the pitch in the axial direction of the teeth in the rotor axial direction, the effect thereof cannot be sufficiently obtained.
In the above-described embodiment, the case where the male rotor side suction flow passage 26A is formed such that the area V1 (see fig. 3) of each flow passage cross section, which is a cross section in the rotor axial direction taken along each radial direction of the male rotor 11A, is larger than the area S1 (see fig. 5) of the rotor radial direction cross section (in other words, a cross section extending in the rotor radial direction) of each working chamber on the male rotor side, and the female rotor side suction flow passage 26B is formed such that the area V2 (see fig. 3) of each flow passage cross section taken along each radial direction of the female rotor 11B is larger than the area S2 (see fig. 5) of the rotor radial direction cross section of each working chamber on the female rotor side is exemplified, but the present invention is not limited thereto. A modification of the present invention will be described with reference to fig. 6. Fig. 6 is a horizontal sectional view showing the structure of the compressor main body according to the present modification.
In the present modification, the male rotor-side suction flow passage 26A is formed such that the area V1 (see fig. 6) of each flow passage cross section, which is a cross section in the axial direction of the rotor divided in each radial direction of the male rotor 11A, is equal to the cross section S1 (see fig. 5) in the radial direction of the rotor of each working chamber on the male rotor side, in a range from at least the virtual plane C in the rotational direction of the male rotor 11A to the pitch (90 degrees in the present embodiment) in the rotational direction of the teeth 13A of the male rotor 11A. In addition, the rotational direction pitch of the teeth means an angle between adjacent tooth tips in the rotational direction of the rotor. In consideration of machining errors and the like, the area V1 is the same as the area S1, that is, the area V1 is in the range of 95% to 105% of the area S1.
The female rotor-side suction flow passage 26B is formed such that the area V2 (see fig. 6) of each flow passage cross section, which is a cross section in the axial direction of the rotor taken along each radial direction of the female rotor 11B in the range from at least the virtual plane C in the rotational direction of the female rotor 11B to the pitch (45 degrees in the present embodiment) in the rotational direction of the teeth 13B of the female rotor 11B, is the same as the cross section S2 (see fig. 5) in the radial direction of the rotor of each working chamber on the female rotor side. In consideration of machining errors and the like, the area V2 is the same as the area S2, that is, the area V2 is in the range of 95% to 105% of the area S2.
In such a modification, a change in the flow velocity in the male rotor side intake flow passage 26A and a change in the flow velocity from the male rotor side intake flow passage 26A to the male rotor side working chamber can be suppressed, and the pressure loss can be further reduced. Further, the change in the flow velocity in the female rotor side suction flow passage 26B and the change in the flow velocity from the female rotor side suction flow passage 26B to the female rotor side working chamber can be suppressed, and the pressure loss can be further reduced.
In the above-described embodiment, the description has been given taking as an example the case where both the male rotor-side intake passage 26A and the female rotor-side intake passage 26B have the feature 1 (specifically, the feature that the passage wall on the outer side in the rotor radial direction is formed so as to be at the same position as the wall of the cylinder chamber 21 when viewed in the rotor axial direction in the range from at least the suction-side end surface of the tooth in the rotor axial direction to half the pitch in the axial direction of the tooth), but the present invention is not limited thereto. That is, only one of the male rotor side suction flow passage 26A and the female rotor side suction flow passage 26B may have the 1 st feature.
In the above-described modification, the case where both the male rotor side suction flow passage 26A and the female rotor side suction flow passage 26B are based on the features 1 and 2 (specifically, the feature that the area of each flow passage cross section, which is a rotor axial cross section that is cut along each radial direction of the rotor, is formed so as to be the same area as the area of the rotor radial cross section of each working chamber in at least the range from the virtual plane C in the rotor rotation direction to the rotation direction pitch of the teeth) has been described as an example, but the present invention is not limited thereto. That is, for example, only one of the male rotor side suction flow passage 26A and the female rotor side suction flow passage 26B may have the 1 st feature and the 2 nd feature. For example, both the male rotor-side suction flow path 26A and the female rotor-side suction flow path 26B may have the 1 st feature, and only one of the male rotor-side suction flow path 26A and the female rotor-side suction flow path 26B may have the 2 nd feature.
Further, although the screw compressor of the oil supply type (specifically, supplying oil into the working chamber) is exemplified as an application object of the present invention, the present invention is not limited to this, and may be a screw compressor of the water supply type (specifically, supplying water into the working chamber) or a screw compressor of the liquid non-supply type (specifically, not supplying liquid such as oil and water into the working chamber).
Description of the reference numerals
11A male rotor
11B female rotor
12 casing
13A, 13B teeth
21 cylinder cavity
22 suction inlet
23 suction flow path
26A male rotor side suction flow path
26B female rotor side suction flow path
27A male rotor side suction flow passage, and flow passage wall on the outer side in the rotor radial direction
27B a flow path wall on the outer side of the suction flow path on the female rotor side in the rotor radial direction.

Claims (6)

1. A screw compressor, comprising:
a male rotor having a tooth;
a female rotor having teeth meshing with the teeth of the male rotor; and
a housing that houses the male rotor and the female rotor,
the housing has:
cylinder chambers which house the teeth of the male rotor and the teeth of the female rotor and form a working chamber on the male rotor side and a working chamber on the female rotor side in their tooth grooves;
a suction port located on the outer side of the teeth of the male rotor and the teeth of the female rotor in the rotor radial direction; and
a suction flow path formed to connect the suction port and a working chamber of a suction stroke and communicating with the working chamber of the suction stroke in a rotor axial direction,
the suction flow path includes:
a male rotor side suction flow path which is located on the male rotor side and is located on a downstream side of a virtual plane passing through a central axis of the male rotor and a central axis of the female rotor; and
a suction flow path on the female rotor side on the downstream side of the imaginary plane, wherein
The male rotor side suction flow path is formed as follows: the flow path wall on the outer side in the rotor radial direction is located at the same position as the wall of the cylinder chamber when viewed in the rotor axial direction, at least in a range from the suction-side end surface of the tooth portion of the male rotor in the rotor axial direction to half of the pitch in the axial direction of the tooth portion.
2. The screw compressor of claim 1, wherein:
the male rotor side suction flow path is formed as follows: in a range from at least the virtual plane in the rotational direction of the male rotor to the rotational direction pitch of the teeth of the male rotor, an area of each flow path cross section, which is a rotor axial cross section taken along each radial direction of the male rotor, is equal to an area of a rotor radial cross section of each working chamber on the male rotor side.
3. A screw compressor according to claim 1 or 2, wherein:
the female rotor side suction flow path is formed as follows: the flow path wall on the outer side in the rotor radial direction is located at the same position as the wall of the cylinder chamber when viewed in the rotor axial direction, at least in a range from the suction-side end surface of the tooth portion of the female rotor in the rotor axial direction to half of the pitch in the axial direction of the tooth portion.
4. A screw compressor according to claim 3, wherein:
the female rotor side suction flow path is formed as follows: in a range from at least the virtual plane in the rotational direction of the female rotor to the rotational direction pitch of the tooth portion of the female rotor, an area of each flow path cross section, which is a cross section of the female rotor in the axial direction of the rotor divided in each radial direction, is equal to an area of a cross section of each working chamber on the female rotor side in the radial direction of the rotor.
5. A screw compressor, comprising:
a male rotor having a tooth;
a female rotor having teeth meshing with the teeth of the male rotor; and
a housing that houses the male rotor and the female rotor,
the housing has:
cylinder chambers which house the teeth of the male rotor and the teeth of the female rotor and form a working chamber on the male rotor side and a working chamber on the female rotor side in their tooth grooves;
a suction port located on the outer side of the teeth of the male rotor and the teeth of the female rotor in the rotor radial direction; and
a suction flow path formed to connect the suction port and a working chamber of a suction stroke and communicating with the working chamber of the suction stroke in a rotor axial direction,
the suction flow path includes:
a male rotor side suction flow path which is located on the male rotor side and is located on a downstream side of a virtual plane passing through a central axis of the male rotor and a central axis of the female rotor; and
a suction flow path on the female rotor side on the downstream side of the imaginary plane, wherein
The female rotor side suction flow path is formed as follows: the flow path wall on the outer side in the rotor radial direction is located at the same position as the wall of the cylinder chamber when viewed in the rotor axial direction, at least in a range from the suction-side end surface of the tooth portion of the female rotor in the rotor axial direction to half of the pitch in the axial direction of the tooth portion.
6. The screw compressor according to claim 5, wherein:
the female rotor side suction flow path is formed as follows: in a range from at least the virtual plane in the rotational direction of the female rotor to the rotational direction pitch of the tooth portion of the female rotor, an area of each flow path cross section, which is a cross section of the female rotor in the axial direction of the rotor divided in each radial direction, is equal to an area of a cross section of each working chamber on the female rotor side in the radial direction of the rotor.
CN201980079092.8A 2018-12-04 2019-10-01 Screw compressor Pending CN113167275A (en)

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PCT/JP2019/038674 WO2020116007A1 (en) 2018-12-04 2019-10-01 Screw compressor

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116480588A (en) * 2023-04-18 2023-07-25 北京通嘉宏瑞科技有限公司 Stator and vacuum pump

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4671749A (en) * 1984-07-04 1987-06-09 Kabushiki Kaisha Kobe Seiko Sho Screw compressor
WO1998042951A1 (en) * 1997-03-26 1998-10-01 Zakrytoe Aktsionernoe Obschestvo 'nezavisimaya Energetika' Steam-driven propeller engine
CN101900120A (en) * 2009-06-01 2010-12-01 株式会社日立工业设备技术 Screw compressor
CN102261332A (en) * 2010-05-25 2011-11-30 株式会社日立工业设备技术 Screw compressor
JP2012041910A (en) * 2010-08-23 2012-03-01 Hokuetsu Kogyo Co Ltd Intake part structure of screw compressor body
CN108691770A (en) * 2017-04-10 2018-10-23 日立江森自控空调有限公司 Helical-lobe compressor

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2716531T3 (en) 2011-10-07 2019-06-13 Takeda Pharmaceuticals Co 1-arylcarbonyl-4-oxy-piperidine compounds useful for the treatment of neurodegenerative diseases

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4671749A (en) * 1984-07-04 1987-06-09 Kabushiki Kaisha Kobe Seiko Sho Screw compressor
WO1998042951A1 (en) * 1997-03-26 1998-10-01 Zakrytoe Aktsionernoe Obschestvo 'nezavisimaya Energetika' Steam-driven propeller engine
CN101900120A (en) * 2009-06-01 2010-12-01 株式会社日立工业设备技术 Screw compressor
CN102261332A (en) * 2010-05-25 2011-11-30 株式会社日立工业设备技术 Screw compressor
JP2012041910A (en) * 2010-08-23 2012-03-01 Hokuetsu Kogyo Co Ltd Intake part structure of screw compressor body
CN108691770A (en) * 2017-04-10 2018-10-23 日立江森自控空调有限公司 Helical-lobe compressor

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116480588A (en) * 2023-04-18 2023-07-25 北京通嘉宏瑞科技有限公司 Stator and vacuum pump
CN116480588B (en) * 2023-04-18 2024-02-23 北京通嘉宏瑞科技有限公司 Stator and vacuum pump

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JP7189749B2 (en) 2022-12-14
JP2021028474A (en) 2021-02-25

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