WO2015114846A1 - スクリュー圧縮機 - Google Patents
スクリュー圧縮機 Download PDFInfo
- Publication number
- WO2015114846A1 WO2015114846A1 PCT/JP2014/065912 JP2014065912W WO2015114846A1 WO 2015114846 A1 WO2015114846 A1 WO 2015114846A1 JP 2014065912 W JP2014065912 W JP 2014065912W WO 2015114846 A1 WO2015114846 A1 WO 2015114846A1
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- chamber
- pressure
- compression chamber
- screw compressor
- tooth
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Classifications
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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
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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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
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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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0021—Systems for the equilibration of forces acting on the pump
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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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
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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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
Definitions
- the present invention relates to a screw compressor, and more particularly to a structure for preventing the gate rotor from being worn or deformed when the screw compressor is stopped.
- the single screw compressors of Patent Documents 1 and 2 include a screw rotor having a plurality of spiral grooves (tooth grooves) on the outer peripheral surface, and two disk-shaped gate rotors having a plurality of gates (tooth portions). It has.
- the two gate rotors are provided symmetrically with respect to the axis of the screw rotor perpendicular to the axis of the screw rotor.
- Two compression chambers are formed in the cylindrical wall by the inner peripheral surface of the cylindrical wall, the tooth groove of the screw rotor, and the tooth portion of the gate rotor.
- the low pressure side and the high pressure side are connected via a compression chamber composed of a screw rotor and a gate rotor. For this reason, when the single screw compressor stops suddenly, the screw rotor rotates in the opposite direction to that during operation due to the difference between the high and low pressures of the refrigerant, and the high-pressure side refrigerant of the screw rotor passes through the compression chamber to the low pressure of the screw rotor. May flow backward.
- the volume of the compression chamber gradually increases, and the refrigerant in the compression chamber expands and is depressurized. That is, the compression chamber becomes an expansion space, and the pressure in the compression chamber decreases.
- the gate rotor is deformed so as to warp from the gate rotor support provided on the back side toward the compression chamber, and the gate rotor Wear or damage may occur.
- the high pressure side discharge chamber and the low pressure side suction chamber inside the casing are configured to communicate with each other when the screw compressor is stopped, and the refrigerant in the discharge chamber is supplied when the operation is stopped.
- the pressure difference between the high pressure side and the low pressure side is reduced.
- the refrigerant in the discharge chamber is less likely to flow to the suction chamber via the compression chamber, and the reverse rotation of the screw rotor is suppressed, thereby reducing the gate rotor. It is intended to suppress wear.
- JP 2013-136957 A (summary)
- Patent Document 1 even if the high-pressure refrigerant in the discharge chamber is introduced into the suction chamber and the pressure in the discharge chamber and the suction chamber is finally equalized, the pressure in the compression chamber remains low. For this reason, there is a possibility that a differential pressure between the equalized pressure and the pressure in the compression chamber remains. Therefore, the structure of Patent Document 1 may not sufficiently suppress the deformation of the gate rotor.
- Patent Document 2 Since the structure of Patent Document 2 is premised on having an economizer port for introducing refrigerant gas of intermediate pressure into the compression chamber of the screw rotor inside the compressor, it is applied to a compressor having no economizer port. I could't.
- the present invention has been made in view of such problems, and an object thereof is to prevent the gate rotor from being deformed when the screw compressor is stopped and to prevent the gate rotor from being worn or damaged. That is.
- a screw compressor includes a screw rotor in which a plurality of tooth grooves constituting a compression chamber are formed on an outer peripheral surface, and a gate rotor in which a plurality of tooth parts meshed with the tooth grooves are formed on an outer peripheral part.
- a screw compressor including a casing in which a screw rotor is housed, wherein the casing has a compression chamber, a suction chamber through which refrigerant sucked into the compression chamber flows, and refrigerant discharged from the compression chamber flows A discharge chamber that communicates with the compression chamber through a compression chamber side communication passage, and a tooth space chamber that is equivalent in pressure to the compression chamber when the screw compressor is operated.
- a refrigerant gas having a pressure higher than that of the compression chamber is introduced from the groove pressure chamber to the compression chamber.
- the present invention it is possible to suppress the deformation of the gate rotor when the screw compressor is stopped, and it is possible to prevent the gate rotor from being worn or damaged.
- Embodiment 1 FIG.
- the screw compressor according to the first embodiment will be described with reference to the drawings.
- the screw compressor is connected to a refrigeration circuit that performs a vapor compression refrigeration cycle by circulating a refrigerant.
- FIG. 1 is a schematic sectional view of a screw compressor according to Embodiment 1 of the present invention.
- FIG. 2 is a cross-sectional view of a main part of the screw compressor according to Embodiment 1 of the present invention. 1 and 2 and the drawings to be described later, the same reference numerals denote the same or corresponding parts, and this is common throughout the entire specification. Furthermore, the forms of the constituent elements appearing in the entire specification are merely examples and are not limited to these descriptions.
- the screw compressor 1 according to the first embodiment is a single screw compressor.
- the present embodiment is an example of a single screw compressor in which two gate rotors 7 are engaged with one screw rotor 5. Embodiment 1 will be described.
- the screw compressor 1 includes a cylindrical casing 2, a motor 3 accommodated in the casing 2, a screw shaft 4 fixed to the motor 3 and driven to rotate by the motor 3, a screw A screw rotor 5 fixed to the shaft 4 and a bearing 6 that rotatably supports an end portion of the screw shaft 4 on the side not fixed to the motor 3 are provided.
- a pair of gate rotors 7 are arranged on the outer periphery of the screw rotor 5 so as to be symmetric with respect to the screw shaft 4.
- the pair of gate rotor 7 and screw rotor 5 constitute a compression mechanism A.
- a slide valve 8 slidable in the direction of the screw shaft 4 is disposed between the inner peripheral surface of the casing 2 and the screw rotor 5.
- the motor 3 includes a stator 3 a that is inscribed and fixed inside the casing 2, and a motor rotor 3 b that is disposed inside the stator 3 a.
- the motor rotor 3 b is fixed to the screw shaft 4 and is coaxial with the screw rotor 5. Is placed on top.
- the screw rotor 5 has a cylindrical shape, and a plurality of tooth grooves 5a extending in a spiral shape from one end to the other end of the screw rotor 5 are formed on the outer peripheral surface.
- the casing 2 is separated into a suction pressure side (left side in FIG. 1) filled with low-pressure refrigerant gas and a discharge pressure side (right side in FIG. 1) filled with high-pressure refrigerant gas.
- One end side of the screw rotor 5 becomes the refrigerant gas suction side and communicates with the suction pressure side, and the other end side of the screw rotor 5 becomes the refrigerant gas discharge side and the tooth groove 5a communicates with the discharge pressure side.
- the gate rotor 7 has a disk shape, and a plurality of tooth portions 7a are provided on the outer peripheral surface along the circumferential direction.
- the tooth portion 7a of the gate rotor 7 is disposed so as to mesh with the tooth groove 5a of the screw rotor 5, and is surrounded by the tooth groove 5a, the tooth portion 7a of the gate rotor 7, the inner peripheral surface of the casing 2, and the slide valve 8.
- the space is formed as a compression chamber 9 filled with a refrigerant gas to be compressed. Oil for lubricating the bearing 6 and sealing the compression chamber 9 is injected into the compression chamber 9.
- the gate rotor 7 is supported by a gate rotor support 71 on the surface opposite to the compression chamber 9 in the tooth gap 5a.
- the slide valve 8 is slidably provided on the suction pressure side and the discharge pressure side of the screw rotor 5 along the outer peripheral surface of the screw rotor 5, and has an opening 8a at the center. .
- a discharge port connected to the discharge chamber 10 is opened on the inner peripheral surface on the discharge pressure side of the casing 2, and the high-pressure refrigerant gas and oil filled in the compression chamber 9 are opened in the slide valve 8.
- the ink is discharged into the discharge chamber 10 through the portion 8a and the discharge port.
- the discharge chamber 10 is a space in which high-pressure refrigerant gas and oil in the compression chamber 9 are discharged.
- a suction chamber 11 through which the refrigerant sucked into the compression chamber 9 flows, a discharge chamber 10 through which the refrigerant discharged from the compression chamber 9 flows, and a tooth gap pressure chamber 12 are partitioned.
- the suction chamber 11 and the tooth space pressure chamber 12 are partitioned by a partition wall 15, and the tooth space pressure chamber 12 and the discharge chamber 10 are partitioned by a partition wall member 16 that can be attached to and detached from the casing 2.
- the tooth gap pressure chamber 12 communicates with the compression chamber 9 through the communication passage 13, and the communication passage 13 is provided with a throttle mechanism (not shown). (Not shown).
- the compression chamber 9 is the only space communicating with the tooth gap pressure chamber 12, so that the pressure in the tooth gap pressure chamber 12 is equal to that of the compression chamber 9.
- the tooth gap pressure chamber 12 and the suction chamber 11 communicate with each other via the communication path 14.
- the communication path 14 is closed when the screw compressor 1 is in operation, and the pressure in the suction chamber 11 becomes higher than the pressure in the tooth gap pressure chamber 12 after the screw compressor 1 is stopped.
- An opening / closing mechanism 20 for opening the communication path 14 is provided.
- the opening / closing mechanism 20 includes an opening / closing lid 21, an opening / closing rod 22 fixed to the opening / closing lid 21, a compression spring 23, and a nut 24.
- the open / close lid 21 is disposed in the tooth gap pressure chamber 12.
- the open / close rod 22 is slidably inserted into the communication path 14, and its tip protrudes toward the suction chamber 11.
- a nut 24 is connected to the protruding portion, and a compression spring 23 that urges the opening / closing lid 21 toward the partition 15 is disposed between the nut 24 and the partition 15.
- the opening / closing mechanism 20 as described above is attached to the communication passage 14, the opening / closing member fixed to the opening / closing lid 21 in a state where the partition member 16 is not attached between the discharge chamber 10 and the tooth space pressure chamber 12.
- the rod 22 is inserted into the communication path 14 from the tooth gap pressure chamber 12 side.
- tip part of the opening-and-closing rod 22 is protruded to the suction chamber 11 side, and the compression spring 23 is inserted in the outer periphery of the protruding opening-and-closing rod 22 from the suction chamber 11 side.
- the nut 24 is screwed from the tip of the opening / closing rod 22, and the nut 24 is tightened until the compression spring 23 becomes shorter than the natural length and a spring pressure is applied to bias the opening / closing lid 21 toward the partition wall 15. Thereby, the mounting of the opening / closing mechanism 20 on the communication path 14 is completed.
- the partition wall member 16 is mounted between the tooth gap pressure chamber 12 and the discharge chamber 10, so that the suction chamber 11, the discharge chamber 10, and the tooth gap pressure chamber 12 are provided inside the casing. Are partitioned.
- FIG. 3 is an operation explanatory diagram of the screw compressor according to Embodiment 1 of the present invention.
- the screw rotor 5 rotates as the screw shaft 4 rotates.
- the gate rotor 7 also rotates, and the compression mechanism A repeats the suction stroke, the compression stroke, and the discharge stroke.
- the operation of the compression mechanism A will be described by paying attention to the compression chamber 9 shaded in FIG.
- FIG. 3A shows the state of the compression chamber 9 during the suction stroke.
- the tooth groove 5a in which the compression chamber 9 is formed meshes with the tooth portion 7a of the gate rotor 7 located on the lower side of FIG.
- the tooth portion 7a relatively moves toward the end of the tooth groove 5a, whereby the lower gate rotor shown in FIG. 7 rotates in the direction of the white arrow.
- the upper gate rotor 7 shown in FIG. 3 rotates in the opposite direction to the lower gate rotor 7 as indicated by a hollow arrow.
- the compression chamber 9 has the largest volume, communicates with the space on the suction pressure side of the casing 2, and is filled with low-pressure refrigerant gas.
- the pressure in the tooth gap pressure chamber 12 during operation of the screw compressor 1 will be described. Since the tooth gap pressure chamber 12 communicates with the compression chamber 9 through the communication passage 13, the pressure of the tooth gap pressure chamber 12 is equal to that of the compression chamber 9 during operation of the screw compressor 1, and the suction chamber Higher than 11 pressures. For this reason, during the operation of the screw compressor 1, the open / close lid 21 is pressed toward the partition wall 15 by the pressure difference between the pressure in the tooth gap pressure chamber 12 and the pressure in the suction chamber 11 and the biasing force of the compression spring 23. The communication path 14 is closed. As a result, there is no flow of refrigerant gas between the suction chamber 11 and the tooth gap pressure chamber 12, and the compression chamber 9 has a pressure equivalent to that of the tooth gap pressure chamber 12.
- FIG. 4 is a schematic diagram showing a state of the gate rotor during operation of the screw compressor according to Embodiment 1 of the present invention.
- FIG. 5 is an explanatory diagram of a phenomenon in which the gate rotor is deformed. 4 and 5, the arrow indicates the traveling direction of the gate rotor 7 with respect to the tooth gap 5a.
- the gate rotor 7 side is at a high pressure and the gate rotor support 71 side is at a low pressure.
- the provision of the tooth gap pressure chamber 12 makes it possible to suppress deformation and damage of the gate rotor 7 by obtaining the pressure relationship described below.
- the deformation and damage of the gate rotor 7 are largely suppressed in two stages, and each stage will be described below.
- the volume of the compression chamber 9 gradually increases, so that the compression chamber 9 becomes an expansion space. That is, the refrigerant inside the compression chamber 9 expands and is depressurized, and the pressure inside the compression chamber 9 decreases. On the other hand, the pressure in the suction chamber 11 gradually increases.
- the refrigerant gas in the suction chamber 11 (the refrigerant gas having a pressure higher than the pressure in the compression chamber 9) is compressed through the tooth gap pressure chamber 12.
- the pressure flows into the chamber 9 and the pressure in the compression chamber 9 increases.
- the refrigerant gas in the suction chamber 11 is directly introduced into the compression chamber 9 through the communication path 14 and the tooth gap pressure chamber 12, so that the pressure in the compression chamber 9 is sucked into the casing 2. Even if it becomes lower than the pressure on the side, the pressure difference can be made sufficiently small. For this reason, it can prevent that the gate rotor 7 deform
- the tooth gap pressure chamber 12 that communicates with the compression chamber 9 via the communication passage 13 and has a pressure equivalent to that of the compression chamber 9 when the screw compressor 1 is operated is provided.
- the screw compressor 1 is stopped and the screw rotor 5 rotates in the reverse direction to reduce the pressure in the compression chamber 9, the pressure difference between the compression chamber 9 and the tooth space pressure chamber 12 is increased.
- the refrigerant gas was introduced into the compression chamber 9 through the communication path 13. Thereby, it can suppress that the gate rotor 7 deform
- the tooth pressure chamber 12 communicating with the compression chamber 9 is provided, and at the same time as the pressure in the compression chamber 9 starts to drop, the high-pressure refrigerant gas in the tooth pressure chamber 12 is communicated with the communication passage 13.
- the high-pressure refrigerant gas in the tooth gap pressure chamber 12 is introduced into the compression chamber 9 through the communication passage 13 by the differential pressure between the compression chamber 9 and the tooth gap pressure chamber 12. In other words, it is mechanical. Therefore, there is an advantage that it is not necessary to configure a special control circuit because the operation of valves such as a solenoid valve is not required.
- an economizer port is necessary.
- the economizer port is unnecessary, and the present embodiment is used in the screw compressor 1 having no economizer port.
- One technique can be applied.
- FIG. The second embodiment relates to an opening / closing mechanism 30 different from the opening / closing mechanism 20 of the first embodiment.
- the second embodiment will be described focusing on the differences from the first embodiment. Note that the modification applied in the configuration part of the first embodiment is also applied to the same configuration part of the second embodiment. This also applies to the embodiments described later.
- FIG. 6 is a cross-sectional view of a main part of the screw compressor according to the second embodiment of the present invention, in which (a) shows a state where the suction chamber 11 and the tooth gap pressure chamber 12 are partitioned, and (b) Indicates a state in which the suction chamber 11 and the tooth space pressure chamber 12 communicate with each other.
- the opening / closing mechanism 20 according to the first embodiment is a mechanism that opens and closes the communication path 14 by operating the opening / closing rod 22 in parallel with the screw shaft 4, whereas the opening / closing mechanism 30 according to the second embodiment includes: In this mechanism, the open / close rod 22 operates in the direction perpendicular to the screw shaft 4 to open and close the communication path 14.
- an insertion hole 17 that intersects perpendicularly to the communication path 14 is formed in a portion where the communication path 14 is formed in the casing 2.
- the insertion hole 17 is open to the outer peripheral surface of the casing 2, and has a large-diameter insertion hole 17a on the opening surface side and a small-diameter insertion hole 17b having a smaller diameter than the large-diameter insertion hole 17a.
- a step 17c is formed. Further, the opening surface of the insertion hole 17 is closed by a lid 18.
- the opening / closing mechanism 30 includes an opening / closing lid 31 slidably disposed in the large-diameter insertion hole 17a, an opening / closing rod 32 fixed to the opening / closing lid 31 and slidably disposed in the small-diameter insertion hole 17b, and a compression spring 33. And.
- the open / close lid 31 is disposed in the large-diameter insertion hole 17a, and the open / close rod 32 extends toward the small-diameter insertion hole 17b.
- a compression spring 33 that urges the opening / closing lid 31 toward the small diameter insertion hole 17b is disposed between the opening / closing lid 31 and the lid 18 in the large diameter insertion hole 17a.
- the large-diameter insertion hole 17a is divided into a space S1 on the opening / closing lid 31 side and a space S2 on the small-diameter insertion hole 17b side by the opening / closing lid 31, and the space S1 communicates with the suction chamber 11 through the communication path 34.
- S ⁇ b> 2 communicates with the tooth gap pressure chamber 12 through the communication path 35.
- the opening / closing rod 32 is formed with a through hole 36 penetrating in the screw shaft 4 direction.
- the opening / closing mechanism 30 configured as described above, when the screw compressor 1 is operated, the space S1 has the same suction pressure as the pressure of the suction chamber 11 through the communication passage 34, and the space S2 has the communication passage 35 and the tooth gap pressure.
- the pressure is the same as the pressure in the compression chamber 9 through the chamber 12. Therefore, as shown in FIG. 6A, the opening / closing lid 31 moves in a direction away from the step 17c against the urging force of the compression spring 33 due to the pressure in the space S2.
- the through hole 36 of the open / close rod 32 is separated from the inside of the communication passage 14, the communication passage 14 is blocked, and the suction chamber 11 and the tooth gap pressure chamber 12 are not communicated.
- the communication path 14 is opened and closed by the refrigerant pressure and the spring force as in the first embodiment, so that the damage and wear of the gate rotor 7 during the reverse rotation of the screw rotor 5 are the first embodiment.
- the same effect is obtained.
- the opening / closing mechanism 20 when the opening / closing mechanism 20 is attached to the communication path 14, an operation inside the casing 2 is required.
- the insertion hole 17 is opened on the outer peripheral surface of the casing 2. Since each member constituting the opening / closing mechanism 30 can be inserted and mounted through the opening, the assembling property of the opening / closing mechanism 30 is improved as compared with the first embodiment.
- Embodiment 3 FIG.
- the communication passage 14 that communicates the suction chamber 11 and the tooth gap pressure chamber 12 is provided, and the communication passage 14 is opened and closed by the opening / closing mechanism 20, whereas in the third embodiment, the suction chamber 11 and the tooth gap pressure are provided.
- the chamber 12 is not in communication.
- the screw rotor 5 rotates in the reverse direction, the refrigerant gas is introduced into the compression chamber 9 only from the tooth gap pressure chamber 12.
- the third embodiment will be described focusing on the differences from the first embodiment.
- FIG. 7 is a cross-sectional view of main parts of a screw compressor according to Embodiment 3 of the present invention.
- Compression chamber 9 ⁇ Gap space pressure chamber 12 ⁇ Discharge chamber 10 (4)
- the third embodiment does not use the opening / closing mechanism 20 used in the first embodiment, the number of parts can be reduced as compared with the first embodiment.
- Embodiment 4 FIG.
- the opening / closing mechanism 20 is deleted from the first embodiment, and a switching mechanism 40 that allows the tooth space pressure chamber 12 to communicate with the compression chamber 9 or the discharge chamber 10 is provided.
- a switching mechanism 40 that allows the tooth space pressure chamber 12 to communicate with the compression chamber 9 or the discharge chamber 10 is provided.
- FIG. 8 is a cross-sectional view of a main part of a screw compressor according to Embodiment 4 of the present invention.
- the switching mechanism 40 connects the tooth gap pressure chamber 12 and the compression chamber 9 via the outside of the casing 2 and the communication passage 41 that communicates the tooth gap pressure chamber 12 and the discharge chamber 10 via the outside of the casing 2.
- a communication path 42 that communicates, and a switching valve (three-way valve, electromagnetic valve, etc.) 43 that switches the communication destination of the tooth gap pressure chamber 12 to the communication path 41 or the communication path 42 are provided.
- the switching valve 43 is switched by a control device 50 configured with a microcomputer or the like.
- the control device 50 controls the switching valve 43 so that the discharge chamber 10 and the tooth gap pressure chamber 12 communicate with each other, so that the tooth gap pressure chamber 12 has the same pressure as the discharge chamber 10. . Further, after the operation of the screw compressor 1 is stopped, the control device 50 controls the switching valve 43 so that the tooth gap pressure chamber 12 and the compression chamber 9 communicate with each other, and the pressure is the same as that of the discharge chamber 10 during operation. The refrigerant is introduced from the tooth gap pressure chamber 12 into the compression chamber 9.
- the refrigerant gas in the tooth gap pressure chamber 12 that was at the same pressure as the discharge chamber 10 during operation is introduced into the compression chamber 9 after the operation of the screw compressor 1 is stopped. 5, even if the pressure in the compression chamber 9 decreases due to the reverse rotation of 5, the introduction of the refrigerant gas from the tooth space pressure chamber 12 can suppress the decrease in the pressure in the compression chamber 9. Thereby, it can suppress that the pressure of the compression chamber 9 falls rather than the pressure of the suction chamber 11, and that the differential pressure becomes large. Therefore, it is possible to suppress the gate rotor 7 from being deformed or damaged by receiving a pressure in a direction opposite to that during operation. Thereby, the aged fall of the performance by abrasion of the gate rotor 7 can be suppressed.
- the present invention can be applied not only to a constant speed screw compressor having a constant rotation speed but also to an inverter screw compressor having a variable rotation speed.
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Abstract
Description
本実施の形態1に係るスクリュー圧縮機について、図を用いて説明する。なお、スクリュー圧縮機は冷媒を循環させて蒸気圧縮式の冷凍サイクルを行う冷凍回路に接続されている。
ケーシング2の内部には、圧縮室9に吸入される冷媒が流通する吸入室11と、圧縮室9から吐出された冷媒が流通する吐出室10と、歯溝圧室12とが区画形成されている。更に詳しくは、吸入室11と歯溝圧室12とが隔壁15で区画され、歯溝圧室12と吐出室10とがケーシング2に対して着脱自在な隔壁部材16で区画されている。歯溝圧室12は、連通路13を通じて圧縮室9に連通しており、連通路13には絞り機構(図示せず)が設けられ、圧力変動を緩和するため、連通路13には絞り機構(図示せず)を備えている。運転中、歯溝圧室12と連通している空間は圧縮室9のみであるため、歯溝圧室12の圧力は圧縮室9と同等の圧力になる。
図3は、本発明の実施の形態1に係るスクリュー圧縮機の動作説明図である。
スクリュー圧縮機1においてモーター3を起動すると、スクリュー軸4が回転するのに伴ってスクリューローター5が回転する。このスクリューローター5の回転に伴ってゲートローター7も回転し、圧縮機構Aが吸入行程、圧縮行程及び吐出行程を繰り返す。ここでは、図3において網掛けを付した圧縮室9に着目して圧縮機構Aの動作を説明する。
歯溝圧室12は連通路13を通じて圧縮室9に連通しているため、スクリュー圧縮機1の運転時、歯溝圧室12の圧力は圧縮室9と同等の圧力となっており、吸入室11の圧力よりも高くなる。このため、スクリュー圧縮機1の運転中は、歯溝圧室12内の圧力と吸入室11の圧力との差圧と圧縮ばね23の付勢力とによって開閉蓋21が隔壁15側に押圧され、連通路14が閉じた状態となる。その結果、吸入室11と歯溝圧室12との間における冷媒ガスの流出入はなく、圧縮室9は歯溝圧室12と同等の圧力になる。
・・・(1)
スクリュー圧縮機1の運転中は図4に示すように圧縮室9においてゲートローター7側が高圧、ゲートローターサポート71側が低圧となっている。しかし、スクリュー圧縮機1の運転が停止し、スクリューローター5の逆回転によって圧縮室9の中の圧力が吸入室11の圧力よりも低くなると、ゲートローター7には運転時と逆方向の押し付け力が作用する。その結果、図5に示すようにゲートローター7がゲートローターサポート71から離れて圧縮室9側に向かって反るように変形(図5では変形量を誇張して表示)したり、損傷したりするおそれがあった。
スクリュー圧縮機1の運転時の圧力関係は、上記(1)のようになっており、この状態からスクリュー圧縮機1を運転停止させると、上述したようにスクリューローター5が運転時とは逆方向へ回転し、高圧側である吐出室10の冷媒ガスが圧縮室9を通して低圧側である吸入室11へ流れる。
・・・(2)
そして、上記式(2)の圧力関係の状態から更にスクリューローター5が逆回転を続けると、圧縮室9の圧力が更に低下し、その一方で、吸入室11の圧力は徐々に上昇する。そして、式(3)の関係が成立した際、吸入室11と歯溝圧室12との差圧により、開閉蓋21が圧縮ばね23の付勢力に抗って隔壁15から離れる方に移動し、連通路14が開いた状態となる。
・・・(3)
本実施の形態1では、連通路13を介して圧縮室9と連通し、スクリュー圧縮機1の運転時に圧縮室9と同等の圧力となる歯溝圧室12を設けた。そして、スクリュー圧縮機1が運転停止し、スクリューローター5が逆回転して圧縮室9の圧力が低下すると、圧縮室9と歯溝圧室12との差圧によって歯溝圧室12の高圧の冷媒ガスが連通路13を通じて圧縮室9へ導入されるようにした。これにより、ゲートローター7が変形するのを抑え、ゲートローター7の摩耗や損傷を防止できる。
実施の形態2は、実施の形態1の開閉機構20とは異なる開閉機構30に関するものである。以下、実施の形態2が実施の形態1と異なる部分を中心に説明する。なお、実施の形態1の構成部分において適用された変形例は、実施の形態2の同様の構成部分においても同様に適用される。この点は、後述の実施の形態においても同様である。
実施の形態1の開閉機構20は、スクリュー軸4に対して平行に開閉ロッド22が動作して連通路14の開閉を行う機構であったのに対し、実施の形態2の開閉機構30は、スクリュー軸4に対して垂直方向に開閉ロッド22が動作して連通路14の開閉を行う機構である。
実施の形態2は実施の形態1と同様に冷媒圧力とばね力とにより連通路14を開閉するため、スクリューローター5の逆回転時におけるゲートローター7の損傷及び摩耗に対しては実施の形態1と同様の効果を得る。また、実施の形態1では、開閉機構20を連通路14に装着するにあたり、ケーシング2の内部での作業が必要となるが、実施の形態2では、挿通孔17がケーシング2の外周面に開口しており、開閉機構30を構成する各部材をその開口から挿入して装着できるため、実施の形態1より開閉機構30の組立性が向上する。
実施の形態1では吸入室11と歯溝圧室12とを連通する連通路14を備え、開閉機構20により連通路14を開閉するのに対し、実施の形態3では吸入室11と歯溝圧室12とを連通しない構造とする。そして、スクリューローター5の逆回転時は歯溝圧室12からのみ圧縮室9へ冷媒ガスの導入がある構造とする。以下、実施の形態3が実施の形態1と異なる部分を中心に説明する。
スクリュー圧縮機1の運転停止後のスクリューローター5の逆回転時に、圧縮室9、歯溝圧室12、吐出室10において、式(4)の圧力関係が成立する間、歯溝圧室12内の冷媒ガス(圧縮室9の圧力よりも高圧の冷媒ガス)が圧縮室9へ導入される。これにより、圧縮室9の圧力が上昇する。
スクリュー圧縮機1において、冷媒として動作圧力の低い、いわゆる低圧冷媒を使用する等して吐出圧力と吸入圧力の圧力差が小さくなる運転のみ実施する際は、吐出圧力と吸入圧力の圧力差が小さいため、実施の形態1を適用した際に開閉機構20の開閉蓋21が開かない場合がある。このような場合には、開閉機構20自体を削除した構成としてもよい。開閉機構20を削除しても、圧縮室9に連通する歯溝圧室12を設け、式(4)の圧力関係が成立する間、歯溝圧室12内の冷媒ガス(圧縮室9の圧力よりも高圧の冷媒ガス)が圧縮室9へ導入される構成とすることで、ゲートローター7の変形及び損傷を抑制することが可能になる。
実施の形態4は、実施の形態1から開閉機構20を削除すると共に、歯溝圧室12を圧縮室9又は吐出室10に連通させる切替機構40を備えた構成としたものである。以下、実施の形態4が実施の形態1と異なる部分を中心に説明する。
切替機構40は、ケーシング2の外部を介して歯溝圧室12と吐出室10とを連通する連通路41と、同様にケーシング2の外部を介して歯溝圧室12と圧縮室9とを連通する連通路42と、歯溝圧室12の連通先を連通路41又は連通路42に切り替える切替弁(三方弁、電磁弁等)43とを備えている。切替弁43は、マイクロコンピュータ等で構成された制御装置50によって切り替えられる。
実施の形態4によれば、運転中に吐出室10と同一の圧力であった歯溝圧室12の冷媒ガスを、スクリュー圧縮機1の運転停止後に圧縮室9へ導入することにより、スクリューローター5の逆回転により圧縮室9の圧力が低下しても、歯溝圧室12からの冷媒ガスの導入により圧縮室9の圧力の低下を抑えることができる。これにより、圧縮室9の圧力が吸入室11の圧力よりも低下することや、その差圧が大きくなるのを抑制できる。したがって、ゲートローター7が、運転時とは逆方向の圧力を受けて変形したり損傷したりすることを抑制することが可能になる。これにより、ゲートローター7の摩耗による性能の経年低下を抑制できる。
Claims (8)
- 圧縮室を構成する複数条の歯溝が外周面に形成されたスクリューローターと、前記歯溝に噛み合わされる複数の歯部が外周部に形成されたゲートローターと、前記スクリューローターが収容されるケーシングとを備えたスクリュー圧縮機であって、
前記ケーシング内は、前記圧縮室と、前記圧縮室に吸入される冷媒が流通する吸入室と、前記圧縮室から吐出された冷媒が流通する吐出室と、前記圧縮室に圧縮室側連通路を介して連通し、前記スクリュー圧縮機の運転時に前記圧縮室と同等の圧力になる歯溝圧室とを備え、
前記スクリュー圧縮機の運転停止後、前記歯溝圧室から前記圧縮室へ、前記圧縮室よりも高圧の冷媒ガスが導入される
スクリュー圧縮機。 - 前記ケーシングに形成され、前記歯溝圧室と前記吸入室とを連通する吸入室側連通路と、
前記スクリュー圧縮機の運転時に前記吸入室側連通路を閉塞し、前記スクリュー圧縮機の運転停止後に前記吸入室の圧力が前記歯溝圧室の圧力よりも高くなった場合に前記吸入室側連通路を開放する開閉機構とを備えた
請求項1記載のスクリュー圧縮機。 - 前記開閉機構は、前記吸入室と前記歯溝圧室との差圧により前記吸入室側連通路を開閉する機構である
請求項2記載のスクリュー圧縮機。 - 前記開閉機構は、前記スクリューローターの軸方向に動作して前記吸入室側連通路を開閉する機構である
請求項2又は請求項3記載のスクリュー圧縮機。 - 前記開閉機構は、前記スクリューローターの軸方向と直交する方向に動作して前記吸入室側連通路を開閉する機構である
請求項2又は請求項3記載のスクリュー圧縮機。 - 前記ケーシングは、前記吸入室側連通路に直交して交差して延び、前記ケーシングの外周面に開口した挿通孔を有し、前記挿通孔に前記開閉機構が動作可能に配置されている
請求項5記載のスクリュー圧縮機。 - 前記挿通孔は、前記ケーシングの外周面に開口した開口面側の大径挿通孔と前記大径挿通孔よりも径が小さい小径挿通孔とを有し、
前記開閉機構は、前記大径挿通孔に摺動可能に配置され、前記大径挿通孔内を前記開口面側の第1空間と前記小径挿通孔側の第2空間とに区画する開閉蓋と、前記開閉蓋に固定され、前記小径挿通孔に摺動可能に配置された開閉ロッドと、前記第1空間に配置され、前記開閉蓋を前記小径挿通孔側に付勢するばねとを有し、
前記ケーシングは、前記第1空間と前記吸入室とを連通する第1連通路と、前記第2空間と前記歯溝圧室とを連通する第2連通路とを有し、
前記開閉ロッドは、前記スクリューローターの軸方向に貫通する貫通孔を有し、
前記スクリュー圧縮機の運転時、前記ばねの付勢力に抗って前記開閉蓋が前記挿通孔の前記開口面側に移動して前記開閉ロッドの前記貫通孔が前記吸入室側連通路内から離れることにより、前記吸入室側連通路が閉じられ、前記スクリュー圧縮機の運転停止時は、前記第1空間と前記第2空間との圧力差と前記ばねの付勢力とにより前記開閉蓋が前記小径挿通孔側に移動して前記開閉ロッドの前記貫通孔が前記吸入室側連通路内に位置することにより前記吸入室側連通路が開かれる
請求項6記載のスクリュー圧縮機。 - 圧縮室を構成する複数条の歯溝が外周面に形成されたスクリューローターと、前記歯溝に噛み合わされる複数の歯部が外周部に形成されたゲートローターと、前記スクリューローターが収容されるケーシングとを備えたスクリュー圧縮機であって、
前記ケーシング内は、前記圧縮室と、前記圧縮室に吸入される冷媒が流通する吸入室と、前記圧縮室から吐出した冷媒が流通する吐出室と、歯溝圧室とを備えており、
前記歯溝圧室と前記吐出室とを連通する吐出室側連通路と、
前記歯溝圧室と前記圧縮室とを連通する圧縮室側連通路と、
前記スクリュー圧縮機の運転時に前記歯溝圧室の連通先を前記吐出室側連通路に切り替え、前記スクリュー圧縮機の運転停止時に前記歯溝圧室の連通先を前記圧縮室側連通路に切り替える切替機構とを備えた
スクリュー圧縮機。
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WO2020255198A1 (ja) * | 2019-06-17 | 2020-12-24 | 三菱電機株式会社 | 冷凍装置 |
WO2022259866A1 (ja) * | 2021-06-08 | 2022-12-15 | 三菱電機株式会社 | スクリュー圧縮機 |
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JP2013113271A (ja) * | 2011-11-30 | 2013-06-10 | Daikin Industries Ltd | スクリュー圧縮機 |
JP2013136957A (ja) * | 2011-12-28 | 2013-07-11 | Daikin Industries Ltd | スクリュー圧縮機 |
JP2013253543A (ja) * | 2012-06-06 | 2013-12-19 | Daikin Industries Ltd | スクリュー圧縮機 |
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JP2009174520A (ja) * | 2007-12-26 | 2009-08-06 | Daikin Ind Ltd | ゲートロータおよびスクリュー圧縮機 |
CN101925745B (zh) * | 2008-01-23 | 2013-04-10 | 大金工业株式会社 | 螺杆压缩机 |
EP2484910B1 (en) * | 2009-09-30 | 2019-05-15 | Daikin Industries, Ltd. | Screw compressor |
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JP2013113271A (ja) * | 2011-11-30 | 2013-06-10 | Daikin Industries Ltd | スクリュー圧縮機 |
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WO2020255198A1 (ja) * | 2019-06-17 | 2020-12-24 | 三菱電機株式会社 | 冷凍装置 |
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CN105849412A (zh) | 2016-08-10 |
GB2537996A (en) | 2016-11-02 |
JP6121000B2 (ja) | 2017-04-26 |
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