EP3683445B1 - Schraubenverdichter - Google Patents

Schraubenverdichter Download PDF

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Publication number
EP3683445B1
EP3683445B1 EP18874619.2A EP18874619A EP3683445B1 EP 3683445 B1 EP3683445 B1 EP 3683445B1 EP 18874619 A EP18874619 A EP 18874619A EP 3683445 B1 EP3683445 B1 EP 3683445B1
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EP
European Patent Office
Prior art keywords
valve
screw
rotor
valve members
casing
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.)
Active
Application number
EP18874619.2A
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English (en)
French (fr)
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EP3683445A4 (de
EP3683445A1 (de
Inventor
Hiromichi Ueno
Hideki Fujiwara
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.)
Daikin Industries Ltd
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Daikin Industries Ltd
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Publication date
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Publication of EP3683445A1 publication Critical patent/EP3683445A1/de
Publication of EP3683445A4 publication Critical patent/EP3683445A4/de
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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
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/50—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
    • F04C18/52—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves

Definitions

  • the present invention relates to a screw compressor including a screw rotor, a gate rotor, and a slide valve mechanism.
  • Screw compressors have been used as compressors for compressing refrigerant and air.
  • Patent Document 1 discloses a screw compressor (a single-screw compressor) having one screw rotor and one gate rotor.
  • the screw rotor and the gate rotor are housed in a casing.
  • the screw rotor is rotatably inserted into a cylinder formed in a central portion of the casing.
  • the screw rotor has helical screw grooves. Gates of the gate rotor respectively mesh with the screw grooves, thereby defining a compression chamber.
  • the casing has therein a low-pressure chamber and a high-pressure chamber. When the screw rotor rotates, a fluid in the low-pressure chamber is sucked into the compression chamber. After compressed in the compression chamber, the fluid is discharged into the high-pressure chamber.
  • the screw compressor of Patent Document 1 is provided with a slide valve mechanism.
  • the slide valve mechanism has a valve member having an inner surface (the surface positioned inward in the radial direction of the casing) substantially bordering the outer periphery of the screw rotor with an oil film interposed therebetween.
  • the cylinder has a valve housing portion slidably housing the valve member.
  • the valve housing portion has a slide groove (a cylinder opening).
  • the valve member has a cross section formed into an arc shape so as to be fitted into the valve housing portion, and partially has a curved surface recessed along the outer periphery of the screw rotor.
  • the slide valve mechanism is used to control the internal volume ratio of a compression mechanism and to control the operating capacity of the compressor.
  • a discharge-side end face of the valve member is shifted in the axial direction of the screw rotor to adjust the size of the discharge-side cylinder opening, and the timing when the fluid is discharged is adjusted.
  • the size of a bypass cylinder opening that communicates with a bypass passage to return the refrigerant being compressed toward an inlet of the compression chamber is adjusted.
  • Patent documents 2, 3, 5 and 6 disclose a two-gate-rotor screw compressor.
  • patent document 2 differs from the claimed invention in that it does not relate to a one-gate-rotor screw compressor and in that it does not comprise an interlocking mechanism configured to move one of the valve members as a following target member following the target member to be driven.
  • Patent document 4 discloses a screw compressor with two meshing screw rotors and a slide valve mechanism formed by two valve members that move differently from each other.
  • the cylinder opening formed on the discharge side of the valve member constitutes a discharge port as can be seen from the foregoing description.
  • the pressure loss therethrough increases.
  • the flow rate be reduced through increasing the opening area of the discharge port.
  • increasing the size of a valve member (101) as shown in, for example, FIG. 13 to increase the opening area increases the diameter of the valve member (101).
  • the projecting amount (P) by which the valve member (101) projects radially outward from a screw rotor (100) increases, and the size of a valve housing portion housing the valve member (101) also increases. This increases the size of the casing of the screw compressor as well.
  • a first aspect of the invention is directed to a one-gate-rotor single-screw compressor according to claim 1.
  • the plurality of separate valve members (52A, 52B) of the slide valve mechanism (50) are arranged for one compressor. This can reduce the size of these valve members (52A, 52B) even if the opening area of a discharge port is increased. This can substantially prevent the size of the casing (10) of the screw compressor from increasing.
  • each valve housing portion (53A, 53B) has a curved wall (54) projecting radially outward of the screw rotor (30) from the cylinder (25) to have an arc-shaped cross section, the curved wall (54) extending in the axial direction of the screw rotor (30), and an outer peripheral surface of each valve member (52A, 52B) is configured as a curved surface having an arc-shaped cross section, the curved surface being fitted to the curved wall (54) of an associated one of the valve housing portions (53A, 53B).
  • the "arc-shaped cross section" as used herein means an arc-shaped cross section perpendicular to the axis of the valve member.
  • portions of each valve member (52A, 52B) and the associated valve housing portion (53A, 53B) fitted to each other have an arc-shaped cross section. This can simplify the configurations of the valve members (52A, 52B) and the valve housing portions (53A, 53A).
  • the portions of each valve member (52A, 52B) and the associated valve housing portion (53A, 53B) fitted to each other have an arc-shaped cross section without a flat portion or a similar portion. This can also substantially prevent the strength of the casing (10) from decreasing.
  • the screw rotor (30) and the gate rotor (40) are provided as a pair of rotors within the casing (10).
  • the size of the casing (10) of a so-called one gate rotor screw compressor can be effectively reduced.
  • a third aspect of the invention is an embodiment of any one of the first to second aspects.
  • axial displacements of the valve members (52A, 52B) during operation of the slide valve mechanism (50) are different from each other.
  • the axial displacement of each valve member (52A, 52B) is determined, for example, based on the axial displacement of the screw groove (31) at the spot where the valve member (52A, 52B) is provided.
  • the axial displacements of the valve members (52A, 52B) are different from each other.
  • the valve members (52A, 52B) are set to respectively have optimum opening areas, thereby efficiently increasing the area of a discharge port and reducing pressure loss.
  • a fourth aspect of the invention is an embodiment of any one of the first to third aspects.
  • each valve member (52A, 52B) has a high pressure end face (57a, 57b) facing a channel through which a high-pressure fluid compressed in the compression chamber (23) flows into a discharge passage in the casing (10), and the high pressure end faces (57a, 57b) of the valve members (52A, 52B) have different angles of inclination ( ⁇ 1, ⁇ 2).
  • the inclination (the angle of inclination ( ⁇ 1, ⁇ 2)) of the high pressure end face (57a, 57b) of each valve member (52A, 52B) is determined, for example, based on the inclination of the associated screw groove (31) at the spot where the valve member (52A, 52B) is provided.
  • the inclinations (the angles of inclination ( ⁇ 1, ⁇ 2)) of the high pressure end faces (57a, 57b) of the valve members (52A, 52B) are different from each other.
  • the valve members (52A, 52B) are set to respectively have optimum angles of inclination ( ⁇ 1, ⁇ 2), thereby efficiently increasing the area of the discharge port and reducing pressure loss.
  • the slide valve mechanism (50) further includes: a driving mechanism (60) configured to move at least one of the valve members (52A, 52B) as a target member to be driven; and an interlocking mechanism (70) configured to move another one of the valve members (52A, 52B) as a following target member following the target member to be driven.
  • one of the valve members (52A, 52B) to be interlocked is designed to follow the another one thereof to be driven. This facilitates optimizing the displacements of the valve members (52A, 52B) on a member-by-member basis. This can efficiently reduce pressure loss.
  • a fifth aspect of the invention is an embodiment of any one of the first to fourth aspects.
  • the slide valve mechanism (50) is an operating capacity adjusting mechanism configured to return a portion of an intermediate-pressure fluid being compressed through a plurality of bypass passages (59a, 59b) of the casing (10) to an inlet of the compression chamber (23), each valve member (52A, 52B) has a low pressure end face (58a, 58b) facing a channel through which the intermediate-pressure fluid flows out of the compression chamber (23) into an associated one of the bypass passages (59a, 59b), and axial positions of the low pressure end faces (58a, 58b) of the valve members (52A, 52B) are different from each other.
  • a sixth aspect of the invention is an embodiment of the fifth aspect.
  • opening areas of the bypass passages (59a, 59b) respectively corresponding to the valve members (52A, 52B) are determined to be substantially equal to each other.
  • the axial position of the low pressure end face (58a, 58b) of each valve members (52A, 52B) is determined, for example, based on the axial position of the associated screw groove (31) at the spot where the valve member (52A, 52B) is provided.
  • the axial positions of the low pressure end faces (58a, 58b) of the valve members (52A, 52B) are different from each other.
  • the opening areas of the bypass passages (59a, 59b) respectively corresponding to the valve members (52A, 52B) are substantially equal to each other. Since an appropriate amount of refrigerant being compressed is accordingly returned through each of the valve members (52A, 52B) to the low pressure side of the compression mechanism, capacity control can be efficiently performed by unloading.
  • a screw compressor (1) of this embodiment is used for refrigerating and air conditioning.
  • the screw compressor (1) is provided to a refrigerant circuit performing a refrigeration cycle, and compresses a refrigerant.
  • the screw compressor (1) includes a hollow casing (10) and a compression mechanism (20).
  • a substantially central portion of the interior of the casing (10) houses the compression mechanism (20) configured to compress a low-pressure refrigerant.
  • the interior of the casing (10) is partitioned into a low-pressure chamber (11) into which a low-pressure gas refrigerant is introduced from an evaporator (not shown) of a refrigerant circuit and which guides the low-pressure gas to the compression mechanism (20), and a high-pressure chamber (12) into which a high-pressure gas refrigerant that has been discharged from the compression mechanism (20) flows.
  • the compression mechanism (20) is interposed between the low-pressure chamber (11) and the high-pressure chamber (12).
  • An electric motor (15) is fixed inside the casing (10).
  • the electric motor (15) includes a stator (15a), and a rotor (15b) rotating in the stator (15a).
  • the electric motor (15) and the compression mechanism (20) are connected together through a drive shaft (21) serving as a shaft.
  • a bearing holder (27) is provided in the casing (10).
  • the drive shaft (21) has a discharge-side end portion supported by bearings (26) fitted to the bearing holder (27), and an intermediate portion supported by a bearing (28).
  • the compression mechanism (20) includes a cylinder (25) formed in the casing (10), one screw rotor (30) disposed inside the cylinder (25), and one gate rotor (40) meshing with the screw rotor (30).
  • the screw rotor (30) is fitted to the drive shaft (21), and is prevented from rotating around the drive shaft (21) by a key (not shown).
  • the screw compressor (1) of this embodiment is a so-called one gate rotor single-screw compressor including the screw rotor (30) and the gate rotor (40), which are provided as a pair of rotors within the casing (10) as described above.
  • the cylinder (25) with a predetermined thickness is formed in a central portion of the casing (10).
  • the screw rotor (30) is rotatably inserted into the cylinder (25).
  • the cylinder (25) has two surfaces (right and left ends in FIG. 1 ) respectively facing the low-pressure chamber (11) and the high-pressure chamber (12).
  • the cylinder (25) has an end face inclined along the direction in which a plurality of screw grooves (31) described below are twisted, without being formed over the entire periphery of the screw rotor (30).
  • the (three in this embodiment) helical screw grooves (31) are formed on the outer peripheral surface of the screw rotor (30).
  • the screw rotor (30) is rotatably fitted into the cylinder (25), and has teeth each having an outer peripheral surface surrounded by the cylinder (25).
  • the gate rotor (40) is formed into the shape of a disk including a plurality of gates (41) (ten gates in this first embodiment) arranged radially.
  • the gate rotor (40) has an axis that lies on a plane perpendicular to the axis of the screw rotor (30).
  • the gate rotor (40) is configured such that some of its gates (41) pass through a portion of the cylinder (25) to respectively mesh with the screw grooves (31) of the screw rotor (30).
  • the screw rotor (30) is made of metal, and the gate rotor (40) is made of a synthetic resin.
  • the gate rotor (40) is disposed in a gate rotor chamber (14) defined in the casing (10).
  • the gate rotor (40) has a central portion connected to a driven shaft (45) serving as a shaft.
  • the driven shaft (45) is rotatably supported by a bearing (46) provided in the gate rotor chamber (14).
  • the bearing (46) is held in the casing (10) via a bearing housing.
  • a suction cover (16) is fitted to an end face of the casing (10) near the low-pressure chamber (11), and a discharge cover (17) is fitted to an end face of the casing (10) near the high-pressure chamber (12).
  • the gate rotor chamber (14) of the casing (10) is covered with a gate rotor cover (18).
  • a discharge-side portion of the casing (10) is provided with a driving mechanism (60) configured to drive a slide valve mechanism (50) to be described below.
  • the driving mechanism (60) is mounted on a stationary plate (19) of the bearing holder (27).
  • the inner peripheral surface of the cylinder (25), the screw grooves (31) of the screw rotor (30), and the gates (41) of the gate rotor (40) surround a compression chamber (23).
  • a right end portion of the screw rotor (30) shown in FIGS. 1 , 4 , and 5 is close to the suction side thereof, and a left end portion thereof is close to the discharge side thereof.
  • An outer peripheral portion of a suction-side end portion (32) of the screw rotor (30) is tapered.
  • Each screw groove (31) of the screw rotor (30) opens, at its suction-side end portion (32), to the low-pressure chamber (11), and this open portion functions as a suction port of the compression mechanism (20).
  • the rotation of the screw rotor (30) causes the gates (41) of the gate rotor (40) to move with respect to the associated screw grooves (31) of the screw rotor (30).
  • the compression chamber (23) is repeatedly expanded and contracted.
  • a suction stroke, a compression stroke, and a discharge stroke for a refrigerant are sequentially performed.
  • the screw compressor (1) includes a slide valve mechanism (50) configured to adjust the timing when the compression chamber (23) communicates with a discharge port (24) (see FIG. 7 ) to control the internal volume ratio (the ratio of the discharge volume to the suction volume of the compression mechanism (20)).
  • the slide valve mechanism (50) includes a plurality of slide valve sub-mechanisms (in this embodiment, two slide valve sub-mechanisms (first and second slide valve sub-mechanisms (50A) and (50B)) provided for the single compression chamber (23).
  • the slide valve mechanism (50) adjusts the opening area of each of cylinder openings (51) of the cylinder (25) to communicate with the compression chamber (23) defined by the gates (41) meshing with the screw grooves (31).
  • the first slide valve sub-mechanism (50A) adjusts the opening area of a first cylinder opening (51A)
  • the second slide valve sub-mechanism (50B) adjusts the opening area of a second cylinder opening (51B).
  • the slide valve mechanism (50) includes two valve members (52) (first and second valve members (52A) and (52B)), and the same number of valve housing portions (53) (first and second valve housing portions (53A) and (53B)) as that of the valve members (52A, 52B).
  • the valve members (52A, 52B) are each movable with respect to the single compression chamber (23) in the axial direction of the screw rotor (30).
  • the valve housing portions (53A, 53B) are formed in the cylinder (25) of the casing (10) to extend along the axial direction.
  • the valve housing portions (53A, 53B) house the valve members (52A, 52B), respectively.
  • An opening of each valve housing portion (53A, 53B) near the screw rotor (30) constitutes an associated one of the cylinder openings (51A, 51B).
  • Each valve housing portion (53A, 53B) has a curved wall (54) protruding radially outward of the screw rotor (30) from the cylinder (25) to have an arc-shaped cross section and extending in the axial direction of the screw rotor (30).
  • the outer peripheral surface of each valve member (52A, 52B) is configured as a curved surface (55) having an arc-shaped cross section and fitted to the curved wall (54) of the associated valve housing portion (53A, 53B).
  • the "arc-shaped cross section” means an arc-shaped cross section perpendicular to its axial direction.
  • each valve member (52A, 52B) during operation of the slide valve mechanism (50) is determined based on the axial displacement of the associated screw groove (31) at a spot where the valve member (52A, 52B) is provided (an associated one of the points A and B in FIG. 7 ).
  • the axial displacement of the screw groove (31) varies between the spot where the valve member (52A) is provided and the spot where the valve member (52B) is provided.
  • the axial displacements (S1, S2) of the valve members (52A, 52B) are also determined to be different from each other.
  • each valve member (52A, 52B) has a high pressure end face (57a, 57b) facing a channel through which a high-pressure fluid compressed in the compression chamber (23) flows into a discharge passage in the casing (10).
  • the inclination (the angle of inclination ⁇ 1, ⁇ 2 in FIG. 8 ) of the high pressure end face (57a, 57b) of the valve member (52A, 52B) is determined based on the inclination of the associated screw groove (31) at the spot where the valve member (52A, 52B) is provided (an associated one of the points A and B in FIG. 7 ).
  • the inclination of the screw groove (31) continuously changes, and varies between the spot where the valve member (52A) is provided and the spot where the valve member (52B) is provided.
  • the angles ( ⁇ 1, ⁇ 2) of inclination of the high pressure end faces (57a, 57b) of the valve members (52A, 52B) are different from each other.
  • the slide valve mechanism (50) includes a driving mechanism (60) configured to move one (52A) of the valve members (52A, 52B) as a target member to be driven.
  • the driving mechanism (60) is connected to driven portions (56A, 56B) of the valve members (52A, 52B) shown in FIG. 3 to drive the valve members (52A, 52B).
  • the driving mechanism (60) includes a cylinder disposed on the discharge side of the valve members (52A, 52B), and a piston moving forward and backward through the cylinder in the axial direction of the screw rotor (30), although its specific structure is not shown.
  • the cylinder is disposed in the casing (10).
  • the slide valve mechanism (50) includes an interlocking mechanism (70) configured to move the other one (52B) of the valve members (52A, 52B) except the target member to be driven, as a following target member following the target member to be driven ( FIG. 8 ).
  • the interlocking mechanism (70) is configured as a link mechanism.
  • the link mechanism (70) includes link rods (71a, 71b) respectively provided on end faces of the valve members (52B, 52A) on the suction side thereof, and a link arm (73) swingable around a fulcrum pin (72).
  • the link rods (71a, 71b) and the link arm (73) are connected together.
  • the distances (swing radii) from the fulcrum pin (72) to the link rods (71a, 71b) are different from each other.
  • the displacements (strokes (S1, S2)) of the valve members (52A, 52B) during operation of the slide valve mechanism (50) are different from each other.
  • each valve member (52A, 52B) is determined based on the axial displacement of the screw groove (31) at the spot where the valve member (52A, 52B) is provided (an associated one of the points A and B in FIG. 7 ) as described above.
  • a coupling portion between each link rod (71a, 71b) and the link arm (73) includes a pin (74a) provided for the link rod (71a, 71b), and a slit which is formed on the link arm (73) and in which the pin (74a) is to be engaged.
  • the driving mechanism (60) merely needs to be configured to move at least one of the valve members (52) as a target member to be driven, and the interlocking mechanism (70) merely needs to be configured to move remaining ones of the valve members (52) as following target members following the target member to be driven.
  • Adjusting the positions of the valve members (52A, 52B) of the slide valve mechanism (50) allows the positions of the high pressure end faces (57a, 57b) facing the channel through which the high-pressure refrigerant compressed in the compression chamber (23) flows into the discharge passage in the casing (10) to change.
  • This causes the opening area of the cylinder opening formed on the discharge side of the cylinder (25) of the casing (10) to change.
  • the timing when the screw groove (31) communicates with the discharge port (not shown) during the rotation of the screw rotor (30) changes. This allows the internal volume ratio of the compression mechanism (20) to be adjusted.
  • the screw rotor (30) upon actuation of the electric motor, the screw rotor (30) is rotated in conjunction with the rotation of the drive shaft (21).
  • the gate rotor (40) is also rotated in conjunction with the rotation of the screw rotor (30), thereby causing the compression mechanism (20) to repeatedly perform a suction stroke, a compression stroke, and a discharge stroke.
  • the rotation of the screw rotor (30) causes the screw grooves (31) and the gates (41) to move relative to each other. This causes the volume of the compression chamber (23) of the screw compressor (1) to increase and then decrease.
  • the low-pressure gas refrigerant in the low-pressure chamber (11) is sucked into the compression chamber (23) through the suction port (the suction stroke).
  • the gates (41) of the gate rotor (40) define the compression chamber (23) such that the compression chamber (23) is separated from the low-pressure chamber.
  • an action for increasing the volume of the compression chamber (23) ends, and an action for decreasing the volume is started.
  • the volume of the compression chamber (23) is decreasing, the sucked refrigerant is compressed (the compression stroke). Further rotation of the screw rotor (30) allows the compression chamber (23) to move.
  • a discharge-side end of the compression chamber (23) communicates with the discharge port. If the discharge-side end of the compression chamber (23) opens to communicate with the discharge port, a high-pressure gas refrigerant is discharged from the compression chamber (23) to the high-pressure chamber (12) (the discharge stroke).
  • Adjusting the positions of the valve members (52A, 52B) of the slide valve mechanism (50) allows the opening areas of the associated cylinder openings (the openings communicating with the discharge port) (51A, 51B) formed on the discharge side of the cylinder (25) of the casing (10) to change.
  • This change in area triggers a change in the ratio of the discharge volume to the suction volume to adjust the internal volume ratio of the compression mechanism (20), and causes the timing when the screw groove (31) communicates with the discharge port during the rotation of the screw rotor (30) to change.
  • each valve member (52A, 52B) is displaced by an amount corresponding to the axial displacement (S1, S2) of the associated screw groove (31) at the spot where the valve member (52A, 52B) is provided (an associated one of the points A and B in FIG. 7 ), and the displacements of the valve members (52A, 52B) are different from each other.
  • the screw groove (31) (the compression chamber (23)) passing through the high pressure end faces (57a, 57b) to communicate with the discharge port through the valve members (52A, 52B) at substantially the same timing. This allows the area of the discharge opening to be larger than if only one valve member is provided. This reduces the flow rate of discharge gas.
  • the inclination (the angle of inclination ( ⁇ 1, ⁇ 2)) of the high pressure end face (57a, 57b) of each valve member (52A, 52B) is determined based on the inclination of the associated screw groove (31) at the spot where the valve member (52A, 52B) is provided (an associated one of the points A and B in FIG. 7 ).
  • the area of the discharge opening is adjusted while the positions of the high pressure end faces (52a, 52b) of the valve members (57A, 57B) and the angles of inclination ( ⁇ 1, ⁇ 2) are optimized. This more effectively reduces pressure loss.
  • the plurality of (two) separate valve members (52A, 52B) are provided for the slide valve mechanism (50).
  • one compressor includes the plurality of (two) valve members (52A, 52B). This can reduce the size of these valve members (52A, 52B) even if the opening area of the discharge port is increased.
  • the size of the casing (10) of the screw compressor can be substantially prevented from increasing.
  • the valve housing portions (53A, 53B) do not have to be increased in size. This can substantially prevent the rigidity of the casing (10) from decreasing, and makes it less likely to deform the casing (10) that is resisting pressure.
  • the dimensional accuracy of the casing (10) can be substantially prevented from decreasing due to such a deformation.
  • portions of each valve member (52A, 52B) and the associated valve housing portion (53A, 53B) fitted to each other have an arc-shaped cross section. This can simplify the configurations of the valve members (52A, 52B) and the valve housing portions (53A, 53A), and can facilitate machining these members to shorten the machining period. Further, since the valve members (52A, 52B) and the valve housing portions (53A, 53B) have an arc-shaped cross section, the dimensional accuracy of these members is also substantially prevented from decreasing, thereby substantially preventing leakage of refrigerant from causing a reduction in efficiency. In addition, the portions of each valve member (52A, 52B) and the associated valve housing portion (53A, 53B) fitted to each other have an arc shape without a flat portion. This helps substantially prevent the strength of the casing (10) from decreasing.
  • each valve member (52A, 52B) is determined in accordance with the axial displacement of the associated screw groove (31) at the spot corresponding to the valve member (52A, 52B), and the inclination of the high pressure end face (57a, 57b) of the valve member (52A, 52B) is determined in accordance with the inclination of the associated screw groove (31) at the spot corresponding to the valve member (52A, 52B).
  • This can efficiently increase the area of the discharge port, and efficiently reduce pressure loss.
  • one of the valve members (52A, 52B) to be interlocked is designed to follow the other one thereof to be driven. This allows the displacement of each valve member (52A, 52B) to be suitable and efficient for the axial displacement of the associated screw groove (31) at the spot where the valve member (52A, 52B) is provided. This also more effectively reduces pressure loss.
  • FIGS. 9 and 10 show a slide valve mechanism (50) according to a first variation.
  • This slide valve mechanism (50) is used in an operating capacity adjusting mechanism performing an unload operation for returning a portion of an intermediate-pressure gas refrigerant being compressed through bypass passages (59a, 59b) of the casing (10) to an inlet of the compression chamber (23).
  • FIG. 9 shows the states of valve members (52A, 52B) fully loaded without being unloaded.
  • FIG. 10 shows the unloaded states of the valve members (52A, 52B).
  • each valve member (52A, 52B) has a low pressure end face (58a, 58b) facing a channel through which an intermediate-pressure gas refrigerant flows out of the compression chamber (23) into the associated bypass passage (59a, 59b).
  • the low pressure end faces (58a, 58b) of the valve members (52A, 52B) are set not to be axially coplanar but to be axially misaligned.
  • the axial position of the low pressure end face (58a, 58b) of each valve members (52A, 52B) is determined based on the axial position of the associated screw groove (23) at the spot where the valve member (52A, 52B) is provided (an associated one of the points C and D in FIG. 9 ).
  • the positions of the low pressure end faces (58a, 58b) of the valve members (52A, 52B) are determined so that the bypass passages (59a, 59b) of the valve members (52A, 52B) communicating with the screw groove (23) has substantially the same area.
  • valve members (52A, 52B) sliding toward the high pressure side respectively increase the opening areas of cylinder openings (51A, 51B) of the low pressure end faces (58a, 58b) of the valve members (52A, 52B) (the opening areas of the bypass passages (59a, 59b)).
  • the refrigerant returns from the cylinder openings (51A, 51B) at a position during a compression stroke of the compression chamber (23) through the bypass passages (59a, 59B) to the low-pressure chamber (11) of the casing (10).
  • the positions of the low pressure end faces (58a, 58b) of the valve members (52A, 52B) are determined so that the openings of the bypass passages (59a, 59b) for the respective valve members (52A, 52B) communicating with the screw groove (23) has substantially the same area.
  • the refrigerant is returned through the cylinder openings (51A, 51B) on the low-pressure sides of the valve members (52A, 52B) to the low pressure side by substantially the same amount.
  • the refrigerant being compressed returns uniformly through the valve members (52A, 52B) to the low pressure chamber.
  • the amount of the refrigerant returned through one of the valve members to the low pressure side is reduced. Accordingly, in this case, if the valve members (52A, 52B) are displaced by the same amount, the amount of the refrigerant returned (the unloaded amount of the refrigerant) is smaller than that in the slide valve mechanism (50) of the first variation. Thus, according to the slide valve mechanism (50) of the first variation, the refrigerant is returned through the valve members (52A, 52B) by substantially the same amount.
  • the screw compressor (1) including the slide valve mechanism (50) of the first variation also includes the plurality of valve members (52A, 52B) respectively inserted into the plurality of valve housing portions (53A, 53B).
  • This first variation is similar to the first embodiment in that the valve members (52A, 52B) and the valve housing portions (53A, 53B) have an arc-shaped cross section. This substantially prevents the size of the casing from increasing, and substantially prevents the strength of the casing from decreasing.
  • a configuration of an interlocking mechanism (70) according to a second variation shown in FIGS. 11 and 12 is different from that according to the first embodiment shown in FIG. 8 .
  • the interlocking mechanism (70) includes a rack and pinion. Specifically, a combination of a first rack (75a) fixed to a first valve member (52A) and a first pinion (76a) meshing with the first rack (75a), and a combination of a second rack (75b) fixed to a second valve member (52B) and a second pinion (76b) meshing with the second rack (75b) form the interlocking mechanism (70). Each pinion (76a, 76b) is fixed to a pinion shaft (76c).
  • high pressure end faces (57a, 57b) of the valve members (52A, 52B) have different inclinations (angles of inclination ( ⁇ 1, ⁇ 2)).
  • the strokes of the valve members (52A, 52B) are set to be different from each other.
  • the pinions (76a, 76b) used have different pitch diameters.
  • the screw compressor (1) including the slide valve mechanism (50) of the second variation also includes the plurality of valve members (52A, 52B) respectively inserted into the plurality of valve housing portions (53A, 53B).
  • This second variation is similar to the first embodiment in that the valve members (52A, 52B) and the valve housing portions (53A, 53B) have an arc-shaped cross section. This substantially prevents the size of the casing from increasing, and substantially prevents the strength of the casing from decreasing.
  • each valve member (52A, 52B) and the associated valve housing portion (53A, 53B) fitted to each other are curved to have an arc-shaped cross section.
  • these surfaces do not have to be curved to have an arc-shaped cross section.
  • the axial displacements of the valve members (52A, 52B) are different from each other, and the angles of inclination ( ⁇ 1, ⁇ 2) of the high pressure end faces (57a, 57b) of the valve members (52A, 52B) are different from each other.
  • either the axial displacements or the angles of inclinations may be different from each other. Even if the axial displacements of the valve members (52A, 52B) are equal to each other, and the angles of inclination thereof are also equal to each other, the casing (10) can be reduced in size.
  • valve members (52A, 52B) are provided, one of them is driven by a driving mechanism (60), and the other one is allowed to follow the one of them through an interlocking mechanism (70).
  • both of them may be driven by the driving mechanism (60), and may be configured such that their displacements are adjusted through the interlocking mechanism (70).
  • the present disclosure is useful as a screw compressor including a slide valve mechanism.

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

Claims (6)

  1. Ein-Tor-Rotor-Einschraubenverdichter, umfassend:
    einen Einschraubenrotor (30) mit schraubenförmigen Schraubennuten (31);
    einen Tor-Rotor (40) mit Toren (41), die in die Schraubennuten (31) eingreifen, wobei der Einschraubenrotor (30) und der eine Tor-Rotor (40) als ein Paar von Rotoren innerhalb des Gehäuses (10) vorgesehen sind;
    ein Gehäuse (10), das im Inneren einen Zylinder (25) aufweist, in den der Schraubenrotor (30) drehbar eingesetzt ist;
    eine Verdichtungskammer (23), die innerhalb des Zylinders (25) durch den Schraubenrotor (30) und den Tor-Rotor (40), die miteinander kämmen, definiert ist; und
    einen Schieberventilmechanismus (50), der so konfiguriert ist, dass er einen Öffnungsbereich einer Zylinderöffnung (51A, 51B) des Zylinders (25) einstellt, wobei die Zylinderöffnung (51A, 51B) mit der Verdichtungskammer (23) in Verbindung steht, wobei der Schieberventilmechanismus (50) Folgendes enthält:
    eine Vielzahl von Ventilelementen (52A, 52B), die in der Verdichtungskammer (23) angeordnet sind, wobei sich die Ventilelemente (52A, 52B) in einer axialen Richtung des Schraubenrotors (30) bewegen, um den Öffnungsbereich einzustellen;
    eine Vielzahl von Ventilgehäuseabschnitten (53A, 53B) des Gehäuses (10), wobei die Ventilelemente (52A, 52B) separat in entsprechenden der Vielzahl von Ventilgehäuseabschnitten (53A, 53B) untergebracht sind,
    einen Antriebsmechanismus (60), der so konfiguriert ist, dass er mindestens eines der Ventilelemente (52A, 52B) als ein anzutreibendes Zielelement bewegt; und
    einen Verriegelungsmechanismus (70), der so konfiguriert ist, dass er ein anderes der Ventilelemente (52A, 52B) als nachfolgendes Zielelement bewegt, das dem anzutreibenden Zielelement folgt.
  2. Einschraubenverdichter nach Anspruch 1, wobei
    jeder Ventilgehäuseabschnitt (53A, 53B) eine gekrümmte Wand (54) aufweist, die von dem Schraubenrotor (30) radial nach außen von dem Zylinder (25) vorsteht, um einen bogenförmigen Querschnitt zu haben, wobei sich die gekrümmte Wand (54) in der axialen Richtung des Schraubenrotors (30) erstreckt, und
    eine äußere Umfangsfläche jedes Ventilelements (52A, 52B) als eine gekrümmte Fläche mit einem bogenförmigen Querschnitt konfiguriert ist, wobei die gekrümmte Fläche an die gekrümmte Wand (54) eines zugehörigen der Ventilgehäuseabschnitte (53A, 53B) angepasst ist.
  3. Einschraubenverdichter nach Anspruch 1 oder 2, wobei Axialverschiebungen der Ventilelemente (52A, 52B) während des Betriebs des Schiebermechanismus (50) voneinander verschieden sind.
  4. Einschraubenverdichter nach einem der Ansprüche 1 bis 3, wobei
    jedes Ventilelement (52A, 52B) eine Hochdruckendfläche (57a, 57b) aufweist, die einem Kanal zugewandt ist, durch den ein in der Verdichtungskammer (23) komprimiertes Hochdruckfluid in einen Auslasskanal im Gehäuse (10) strömt, und die Hochdruckendflächen (57a, 57b) der Ventilelemente (52A, 52B) unterschiedliche Neigungswinkel (θ1, θ2) aufweisen.
  5. Einschraubenverdichter nach einem der Ansprüche 1 bis 4, wobei
    der Schiebermechanismus (50) ein Mechanismus zur Einstellung der Betriebskapazität ist, der so konfiguriert ist, dass er einen Teil eines Mitteldruckfluids, das komprimiert wird, durch eine Vielzahl von Bypasskanälen (59a, 59b) des Gehäuses (10) zu einem Einlass der Verdichtungskammer (23) zurückführt,
    jedes Ventilelement (52A, 52B) eine Niederdruckendfläche (58a, 58b) aufweist, die einem Kanal zugewandt ist, durch den das Mitteldruckfluid aus der Verdichtungskammer (23) in einen zugehörigen der Bypasskanäle (59a, 59b) strömt, und
    axiale Positionen der Niederdruckendflächen (58a, 58b) der Ventilelemente (52A, 52B) voneinander verschieden sind.
  6. Einschraubenverdichter nach Anspruch 5, wobei
    Öffnungsbereiche der Bypasskanäle (59a, 59b), die jeweils den Ventilelementen (52A, 52B) entsprechen, so bestimmt sind, dass sie im Wesentlichen gleich sind.
EP18874619.2A 2017-10-30 2018-10-17 Schraubenverdichter Active EP3683445B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017208828A JP6500964B1 (ja) 2017-10-30 2017-10-30 スクリュー圧縮機
PCT/JP2018/038630 WO2019087785A1 (ja) 2017-10-30 2018-10-17 スクリュー圧縮機

Publications (3)

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EP3683445A1 EP3683445A1 (de) 2020-07-22
EP3683445A4 EP3683445A4 (de) 2020-12-09
EP3683445B1 true EP3683445B1 (de) 2023-11-08

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JP (1) JP6500964B1 (de)
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JP7128426B1 (ja) * 2021-03-31 2022-08-31 ダイキン工業株式会社 圧縮機

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Publication number Priority date Publication date Assignee Title
GB429878A (en) * 1934-01-03 1935-06-07 Paul Eckert Good Improvements in rotary compressors and pumps
FR2398901A1 (fr) * 1977-07-29 1979-02-23 Zimmern Bernard Regulation des compresseurs a vis par soulevement de pignon
US4610612A (en) * 1985-06-03 1986-09-09 Vilter Manufacturing Corporation Rotary screw gas compressor having dual slide valves
US4704069A (en) * 1986-09-16 1987-11-03 Vilter Manufacturing Corporation Method for operating dual slide valve rotary gas compressor
JPH0780135B2 (ja) 1990-04-18 1995-08-30 コクヨ株式会社 ステープル除去具
US7891955B2 (en) * 2007-02-22 2011-02-22 Vilter Manufacturing Llc Compressor having a dual slide valve assembly
JP4183015B1 (ja) * 2007-06-22 2008-11-19 ダイキン工業株式会社 シングルスクリュー圧縮機およびその組立方法
JP4645754B2 (ja) * 2009-06-15 2011-03-09 ダイキン工業株式会社 スクリュー圧縮機
BR112013006770A2 (pt) * 2010-09-30 2020-12-15 Daikin Industries Ltd. Compressor de rosca
JP2012197734A (ja) * 2011-03-22 2012-10-18 Daikin Industries Ltd スクリュー圧縮機
JP2013177868A (ja) * 2012-02-29 2013-09-09 Daikin Industries Ltd スクリュー圧縮機
JP2014029133A (ja) * 2012-07-31 2014-02-13 Mitsubishi Electric Corp スクリュー圧縮機
JP2014047708A (ja) * 2012-08-31 2014-03-17 Mitsubishi Electric Corp スクリュー圧縮機
JPWO2017094057A1 (ja) * 2015-11-30 2018-07-12 三菱電機株式会社 シングルスクリュー圧縮機および冷凍サイクル装置
WO2017175298A1 (ja) * 2016-04-05 2017-10-12 三菱電機株式会社 スクリュー圧縮機および冷凍サイクル装置
EP3440358B9 (de) * 2016-04-06 2022-03-23 BITZER Kühlmaschinenbau GmbH Schraubenverdichter
CN206419206U (zh) * 2017-01-10 2017-08-18 麦克维尔空调制冷(苏州)有限公司 非对称滑阀式单螺杆制冷压缩机

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Publication number Publication date
EP3683445A4 (de) 2020-12-09
JP6500964B1 (ja) 2019-04-17
CN111183288A (zh) 2020-05-19
WO2019087785A1 (ja) 2019-05-09
JP2019082123A (ja) 2019-05-30
EP3683445A1 (de) 2020-07-22
CN111183288B (zh) 2021-03-26

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