EP3842641B1 - Screw compressor - Google Patents
Screw compressor Download PDFInfo
- Publication number
- EP3842641B1 EP3842641B1 EP18930891.9A EP18930891A EP3842641B1 EP 3842641 B1 EP3842641 B1 EP 3842641B1 EP 18930891 A EP18930891 A EP 18930891A EP 3842641 B1 EP3842641 B1 EP 3842641B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- screw
- rotor
- slide
- casing
- screw compressor
- 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.)
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Links
- 230000006835 compression Effects 0.000 claims description 47
- 238000007906 compression Methods 0.000 claims description 47
- 238000005266 casting Methods 0.000 claims description 12
- 239000003507 refrigerant Substances 0.000 description 14
- 238000010586 diagram Methods 0.000 description 6
- 230000003111 delayed effect Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Images
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
- 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
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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
- F04C2230/00—Manufacture
- F04C2230/20—Manufacture essentially without removing material
- F04C2230/21—Manufacture essentially without removing material by casting
-
- 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
- F04C2240/00—Components
- F04C2240/30—Casings or housings
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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
- F04C2240/00—Components
- F04C2240/40—Electric motor
-
- 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
- F04C2240/00—Components
- F04C2240/50—Bearings
Definitions
- the present invention relates to a screw compressor for use in compression of refrigerant in, for example, a refrigeration machine.
- a screw compressor is known as a given type of positive-displacement compressor and used as a component of a refrigerant circuit that is included in, for example, a refrigeration machine.
- a single-screw compressor is known, and a casing of the single-screw compressor houses a single screw rotor and two gate rotors.
- the screw rotor has spiral tooth-grooves, and the two gate rotors each have gate-rotor teeth that are fitted in the tooth grooves of the screw rotor.
- compression chambers are formed by engagement of the tooth grooves of the screw rotor and gate-rotor teeth of each of the gate rotors.
- One of ends of the screw rotor in a direction along the rotation axis of the screw rotor is located on a refrigerant suction side, and the other end is located on a refrigerant discharge side.
- the interior of the casing is divided into a low-pressure space provided on the suction side of each of the compression chamber and a high-pressure space provided on the discharge side of each compression chamber.
- the screw rotor is fixed to a screw shaft to be rotated by a driving unit provided in the casing.
- One of end portions of the screw shaft is supported by a bearing housing that includes an internal bearing therein such that the above one end portion can be rotated, and the other end portion is joined to the driving unit.
- refrigerant in the low-pressure space is sucked into the compression chamber, compressed in the compression chamber, and then discharged into the high-pressure space.
- Another type of screw compressor includes a pair of slide valves that are provided in a slide groove formed in an inner cylindrical surface of a casing, and that are slidable in a direction along the rotation axis of a screw rotor.
- the slide valves are provided to change an internal volume ratio.
- the slide valves are each slid in the direction along the rotation axis of the screw rotor to change the start position of discharging of high-pressure gas refrigerant obtained through compression in a compression chamber, and thereby change the timing of opening of a discharge port.
- the slide valves each include a valve body that faces the screw rotor and a guide that forms a slide surface in such a manner as to face an outer circumferential surface of a bearing housing.
- a predetermined space is provided between the screw rotor and the valve body of each slide valve to avoid occurrence of, for example, seizure, by preventing the screw rotor and the valve body from contacting each other when, for example, the screw compressor is assembled or the screw compressor is in operation.
- Patent Literature 2 which forms the basis for the preamble of claim 1, discloses a screw compressor including a casing, a screw rotor disposed in a cylinder portion of the casing to define a compression chamber, and a capacity control slide valve. Fluid sucked into the compression chamber is compressed by rotation of the screw rotor.
- the slide valve is slidable along a rotation axis of the screw rotor and is opposed to an outer circumferential surface of the screw rotor.
- the slide valve includes a dynamic pressure generator formed on an opposed surface of the slide valve that is opposed to the screw rotor to generate a dynamic pressure using fluid in contact with the opposed surface of the slide valve.
- the slide valve is configured so that the dynamic pressure generated by the dynamic pressure generator avoids contact between the slide valve and the screw rotor.
- a casing bore needs to accommodate a bearing housing.
- the outside diameter of the bearing housing needs to be less than the inside diameter of the casing bore, and a space is provided between the bearing housing and the slide valve.
- the screw rotor when the temperature of refrigerant gas compressed in the compression chamber rises, the screw rotor thermally expands, and the space between the outer circumferential surface of the screw rotor and the inner cylindrical surface of the casing and the space between the outer circumferential surface of the screw rotor and the slide valve may decrease.
- the screw rotor may rotate backward due to a pressure differential between high pressure and low pressure in the casing.
- valve body of the slide valve tilts toward the screw rotor or rotate in the circumferential direction. Consequently, part of the valve body of the slide valve may project from the inner circumferential surface of the casing bore and come into contact with the screw rotor, and may thus cause seizure or other problems.
- the present invention is applied to solve the above problem, and relates to a screw compressor that is capable of preventing a slide valve and a screw rotor from coming into contact with each other, and has a high reliability.
- a screw compressor includes: a casing that forms an outer shell of the screw compressor; a screw shaft provided in the casing and configured to be rotated by driving; a screw rotor fixed to the screw shaft and having spiral tooth grooves formed in an outer circumferential surface of the screw rotor; a gate rotor having a plurality of gate-rotor teeth that fit in the spiral tooth grooves of the screw rotor, the gate rotor defining together with the casing and the screw rotor, a compression chamber; a slide valve provided in a slide groove formed in an inner cylindrical surface of the casing, and configured to be slidable in a direction along a rotation axis of the screw rotor; and a bearing housing including an internal bearing that supports one end portion of the screw shaft in such a manner as to allow the end portion of the screw shaft to be rotated.
- the slide valve includes a valve body and a guide, connected to each other by a connection portion, the valve body being located on one side of the slide valve in a slide direction of the slide valve and facing the screw rotor, the guide being located on an other side of the slide valve in the slide direction of the slide valve and having a slide surface that faces an outer circumferential surface of the bearing housing.
- a raised surface portion is formed at an outer circumferential surface of the bearing housing and protrudes toward the slide surface of the guide of the slide valve.
- the raised surface portion comes into contact with and supports the slide valve that has a valve body, which would tilt toward the screw rotor or rotate in a circumferential direction if the raised surface portion were not provided. It is therefore possible to prevent the slide valve from coming into contact with the screw rotor, and to hence provide a screw compressor having a high reliability.
- Fig. 1 is a sectional view illustrating an internal configuration of a screw compressor according to an embodiment of the present invention.
- Fig. 2 is an enlarged sectional view of related portions that is taken along line A-A indicated by arrows in Fig. 1 .
- Fig. 3 is an enlarged sectional view of the related portions that is taken along line B-B indicated by arrows in Fig. 1 .
- Fig. 4 is a perspective view of a bearing housing of the screw compressor according to the embodiment of the present invention.
- a screw compressor 100 will be described by referring to by way of example the case where the screw compressor 100 is a single-stage single-screw compressor.
- the screw compressor 100 includes a casing 1, a compression unit 2, and a driving unit 3.
- the casing 1 is cylindrical and forms an outer shell of the screw compressor 100.
- the compression unit 2 and the driving unit 3 are provided in the casing 1.
- the interior of the casing 1 is divided into a low-pressure space 10 and a high-pressure space 11.
- the compression unit 2 includes a screw shaft 4, a screw rotor 5, a pair of gate rotors 6, gate-rotor supports (not illustrated), a pair of slide valves 7, and a bearing housing 8.
- the screw rotor 5 is fixed to the screw shaft 4.
- the bearing housing 8 includes a bearing 80 that supports an end portion of the screw shaft 4 to allow the end portion to be rotated.
- the screw shaft 4 is provided in the casing 1 and can be driven to rotate by the driving unit 3.
- the screw shaft 4 extends in a direction along a tube axis of the casing 1.
- One of end portions of the screw shaft 4 is supported by the bearing 80, which faces the discharge side of the screw rotor 5, such that the above one end portion can be rotated, and the other end portion is joined to the driving unit 3.
- the screw rotor 5 has spiral tooth grooves 5a formed in an outer circumferential surface of a cylinder.
- the screw rotor 5 is fixed to the screw shaft 4 and can be rotated together with the screw shaft 4 by the driving unit 3.
- a side of the screw rotor 5 that adjoins the low-pressure space 10 is a refrigerant-suction side for refrigerant
- an end of the screw rotor 5 that adjoins the high-pressure space 11 is a refrigerant-discharge side for the refrigerant.
- a predetermined space S is provided between the screw rotor 5 and each of the slide valves 7. This is intended to avoid occurrence of, for example, seizure, by preventing the slide valve 7 and the screw rotor 5 from contacting each other, for example, when the screw compressor 100 is assembled or during an operation of the screw compressor 100.
- gate-rotor teeth 6a are formed at outer peripheral portions of the gate rotors 6, and mesh with and fit in the tooth grooves 5a of the screw rotor 5. As illustrated in Fig. 1 , the pair of gate rotors 6 are located to hold the screw rotor 5 in a radial direction. In the compression unit 2, the tooth grooves 5a of the screw rotor 5 and the gate-rotor teeth 6a of the gate rotor 6 mesh with each other, thereby forming compression chambers 20. To be more specific, in the screw compressor 100, the two gate rotors 6 are provided on opposite sides of the screw rotor 5, that is, the gate rotors 6 are displaced from each other by180 degrees.
- the number of the above compression chambers 20 is two, and one of the compression chambers 20 is located on an upper side of the screw shaft 4, and the other is located on a lower side of the screw shaft 4.
- the gate-rotor supports (not illustrated) have gate-rotor-support teeth that are located to face the gate-rotor teeth 6a, and support the gate rotors 6.
- each of the slide valves 7 is provided in a slide groove 12 formed in the inner cylindrical surface of the casing 1 and is slidable in the direction along the rotation axis of the screw rotor 5.
- the slide valve 7 is, for example, an internal-volume-ratio regulating valve.
- the slide valve 7 includes a valve body 70 and a guide 71.
- the valve body 70 is located to face the screw rotor 5, and the guide 71 has a slide surface that faces an outer circumferential surface of the bearing housing 8.
- the valve body 70 and the guide 71 are connected to each other by a connection portion 72.
- a discharge port 7a is provided between the valve body 70 and the guide 71 to allow refrigerant compressed in the compression chamber 20 to be discharged from the discharge port 7a.
- the refrigerant discharged from the discharge port 7a is discharged into the high-pressure space (not illustrated) through a discharge gas passage.
- the slide valve 7 is connected to a slide-valve driving device 74 by a rod 73 fixed to the end face of the guide 71.
- the slide-valve driving device 74 is, for example, a device that is driven by a gas pressure, a device that is driven by an oil pressure, or a device that is driven by a motor.
- a discharge timing at which refrigerant sucked into the compression chamber 20 is discharged is adjusted.
- the discharge timing can be advanced, and when the slide valve 7 is slid toward the discharge side to delay the opening timing of the discharge port 7a, the discharge timing can be delayed.
- the discharge timing is advanced, the screw compressor 100 is operated at a low internal volume ratio, and when the discharge timing is delayed, the screw compressor 100 is operated at a high internal volume ratio.
- the bearing housing 8 is provided close to an end portion of the screw rotor 5 that is located on the discharge side.
- the outside diameter of the bearing housing 8 is greater than the outside diameter of the screw rotor 5. Furthermore, since the bearing housing 8 needs to be into a casing bore 13 that accommodate the screw rotor 5, the outside diameter of the bearing housing 8 is less than the inside diameter of the casing bore 13. It should be noted that the outside diameter of the bearing housing 8 may be less than the outside diameter of the screw rotor 5.
- two raised surface portions 81 and recessed surface portions 82 are formed at the outer circumferential surface of the bearing housing 8.
- the raised surface portions 81 protrude toward the guides 71 of the slide valves 7.
- the recessed surface portions 82 are formed in the same circumferential direction as the raised surface portions 81.
- the raised surface portions 81 are located within the movable range of the slide valve 7.
- the outside diameter of the raised surface portions 81 is, for example, greater than or equal to the inside diameter of the casing bore 13 that accommodates the screw rotor 5.
- the outside diameter of the recessed surface portions 82 is, for example, less than the inside diameter of the casing bore 13.
- the bearing housing 8 is formed in advance, by use of a casting mold, to have recessed surface portions 82 at the outer circumferential portion of the bearing housing 8, and raised surface portions 81 are then formed by cutting both sides of each of the recessed surface portions 82 using a lathe machine in such a manner as to extend in the same circumferential direction as the recessed surface portions 82. That is, the recessed surface portions 82 are portions that are used to form the raised surface portions 81 using the lathe machine. It should be noted that the surfaces of the recessed surface portions 82 are casting surface portions 82a formed by the casting mold. Since the recessed surface portions 82 are portions that do not particularly function in the screw compressor 100, it is no problem to keep the surfaces of the recessed surface portions 82 as the casting surfaces 82a.
- the driving unit 3 includes an electric motor 30.
- the electric motor 30 includes a stator 31 and a motor rotor 32.
- the stator 31 is inscribed in the casing 1, fixed to an inner surface of the casing 1, and has space in the radial direction.
- the motor rotor 32 is provided inward of the stator 31 such that the motor rotor 32 can be rotated.
- the motor rotor 32 is connected to an end portion of the screw shaft 4, and is located on the same axis as the screw rotor.
- the screw rotor 5 is also rotated. It should be noted that the electric motor 30 is driven such that the rotational speed of the electric motor 30 can be changed by an inverter (not illustrated), and is thus driven to increase/decrease the rotational speed of the screw shaft 4.
- Fig. 5 is an explanatory diagram of a suction step during an operation of the compression unit of the screw compressor according to the embodiment of the present invention.
- Fig. 6 is an explanatory diagram of a compression step during the operation of the compression unit of the screw compressor according to the embodiment of the present invention.
- Fig. 7 is an explanatory diagram of a discharge step during the operation of the compression unit of the screw compressor according to the embodiment of the present invention. It should be noted that the steps will be described while paying attention to the compression chamber 20 indicated by a dot hatch pattern in each of Figs. 5 to 7 .
- Fig. 5 illustrates the state of the compression chamber 20 in the suction step.
- the screw rotor 5 is driven by the electric motor 30 to rotate in a direction indicated by a solid arrow in the figure.
- the volume of the compression chamber 20 is decreased as illustrated in Fig. 6 .
- the bearing housing 8 is designed to have an outside diameter less than the inside diameter of the casing bore 13, since the bearing housing 8 needs to be accommodated in the bearing housing 8.
- the screw rotor 5 may thermally expand, and as a result the space between the outer circumferential surface of the screw rotor 5 and the inner cylindrical surface of the casing 1 and the space between the outer circumferential surface of the screw rotor 5 and each of the slide valves 7 may decrease.
- the screw rotor 5 may rotate backward because of a pressure differential between high pressure and low pressure in the casing 1.
- the screw compressor 100 is formed to include: the casing 1 that forms the outer shell of the screw compressor 100; the screw shaft 4 that is provided in the casing 1 and rotated by driving; the screw rotor 5 that is fixed to the screw shaft 4 and has the spiral tooth grooves 5a formed in the outer circumferential surface of the screw rotor 5; and the gate rotors 6 that have gate-rotor teeth 6a to be fitted in the spiral tooth grooves 5a, and that defines together with the casing 1 and the screw rotor 5, the compression chamber 20.
- the screw compressor 100 includes: the slide valves 7 that are provided in the slide groove 12 formed in the inner cylindrical surface of the casing 1, and that are slidable in the direction along the rotation axis of the screw rotor 5; and the bearing housing 8 including the internal bearing 80 that rotatably supports one end portion of the screw shaft 4.
- the raised surface portions 81 are formed at the outer circumferential surface of the bearing housing 8 and protrude toward the slide surfaces of the slide valves 7.
- valve bodies 70 of the slide valves 7 may tilt toward the screw rotor 5 or rotate in the circumferential direction, since in the screw compressor 100 according to the embodiment, the raised surface portions 81 come into contact with and support the slide valves 7, it is possible to prevent the slide valves 7 from coming into contact with the screw rotor 5. Accordingly, it is possible to provide a screw compressor having a high reliability.
- an outside diameter of the raised surface portions 81 is greater than or equal to the inside diameter of the casing bore 13 that accommodates the screw rotor 5.
- the recessed surface portions 82 are formed in the same circumferential direction as the raised surface portions 81.
- the outside diameter of the recessed surface portions 82 is less than the inside diameter of the casing bore 13.
- the surfaces of the recessed surface portions 82 are the casting surfaces 82a formed by the casting mold. That is, in the recessed surface portion 82, which does not particularly function in the structure of the screw compressor 100, the surfaces of the casting surfaces 82a are kept as the casting surfaces 82a. Thus, as additional processing does not need to be performed on the recessed surface portions 82. It is therefore possible to reduce the manufacturing cost and improve the productivity.
- the internal configuration of the screw compressor 100 is not limited to that explained in the above descriptions, and the screw compressor 100 may include other components.
- the screw compressor 100 is described as a single-stage single-screw compressor. However, this is an example; that is, the screw compressor 100 may be a two-stage single-screw compressor.
- each of the slide valves 7 is not limited to an internal-volume-ratio regulating valve, and may be, for example, a valve configured to regulate a compression capacity.
- the number of gate rotors 6 is not limited to two, and one gate rotor 6 may be provided.
- the subject matter of the present invention covers design changes and various applications normally implemented by a person with ordinary skill in the art, as long as they still fall within the scope of the present invention as defined by the appended claims.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
- The present invention relates to a screw compressor for use in compression of refrigerant in, for example, a refrigeration machine.
- As disclosed in
Patent Literature 1, a screw compressor is known as a given type of positive-displacement compressor and used as a component of a refrigerant circuit that is included in, for example, a refrigeration machine. For example, as such a screw compressor, a single-screw compressor is known, and a casing of the single-screw compressor houses a single screw rotor and two gate rotors. The screw rotor has spiral tooth-grooves, and the two gate rotors each have gate-rotor teeth that are fitted in the tooth grooves of the screw rotor. In the single-screw compressor, compression chambers are formed by engagement of the tooth grooves of the screw rotor and gate-rotor teeth of each of the gate rotors. One of ends of the screw rotor in a direction along the rotation axis of the screw rotor is located on a refrigerant suction side, and the other end is located on a refrigerant discharge side. The interior of the casing is divided into a low-pressure space provided on the suction side of each of the compression chamber and a high-pressure space provided on the discharge side of each compression chamber. - The screw rotor is fixed to a screw shaft to be rotated by a driving unit provided in the casing. One of end portions of the screw shaft is supported by a bearing housing that includes an internal bearing therein such that the above one end portion can be rotated, and the other end portion is joined to the driving unit. In the screw compressor, when the screw rotor is driven to rotate by the driving unit, with the screw shaft interposed between the screw rotor and the driving unit, refrigerant in the low-pressure space is sucked into the compression chamber, compressed in the compression chamber, and then discharged into the high-pressure space.
- Another type of screw compressor includes a pair of slide valves that are provided in a slide groove formed in an inner cylindrical surface of a casing, and that are slidable in a direction along the rotation axis of a screw rotor. The slide valves are provided to change an internal volume ratio. To be more specific, the slide valves are each slid in the direction along the rotation axis of the screw rotor to change the start position of discharging of high-pressure gas refrigerant obtained through compression in a compression chamber, and thereby change the timing of opening of a discharge port. The slide valves each include a valve body that faces the screw rotor and a guide that forms a slide surface in such a manner as to face an outer circumferential surface of a bearing housing. Between the screw rotor and the valve body of each slide valve, a predetermined space is provided to avoid occurrence of, for example, seizure, by preventing the screw rotor and the valve body from contacting each other when, for example, the screw compressor is assembled or the screw compressor is in operation.
-
Patent Literature 2, which forms the basis for the preamble ofclaim 1, discloses a screw compressor including a casing, a screw rotor disposed in a cylinder portion of the casing to define a compression chamber, and a capacity control slide valve. Fluid sucked into the compression chamber is compressed by rotation of the screw rotor. The slide valve is slidable along a rotation axis of the screw rotor and is opposed to an outer circumferential surface of the screw rotor. The slide valve includes a dynamic pressure generator formed on an opposed surface of the slide valve that is opposed to the screw rotor to generate a dynamic pressure using fluid in contact with the opposed surface of the slide valve. The slide valve is configured so that the dynamic pressure generated by the dynamic pressure generator avoids contact between the slide valve and the screw rotor. -
- Patent Literature 1:
Japanese Patent No. 4301345 - Patent Literature 2:
US 2010/260620 A1 - In the screw compressor disclosed in
Patent Literature 1, a casing bore needs to accommodate a bearing housing. Thus, the outside diameter of the bearing housing needs to be less than the inside diameter of the casing bore, and a space is provided between the bearing housing and the slide valve. Meanwhile, in the screw compressor, when the temperature of refrigerant gas compressed in the compression chamber rises, the screw rotor thermally expands, and the space between the outer circumferential surface of the screw rotor and the inner cylindrical surface of the casing and the space between the outer circumferential surface of the screw rotor and the slide valve may decrease. In addition, after the operation of the screw compressor is stopped, the screw rotor may rotate backward due to a pressure differential between high pressure and low pressure in the casing. When the screw rotor rotates backward, for example, the internal pressure of the compression chamber changes, the valve body of the slide valve tilts toward the screw rotor or rotate in the circumferential direction. Consequently, part of the valve body of the slide valve may project from the inner circumferential surface of the casing bore and come into contact with the screw rotor, and may thus cause seizure or other problems. - The present invention is applied to solve the above problem, and relates to a screw compressor that is capable of preventing a slide valve and a screw rotor from coming into contact with each other, and has a high reliability.
- A screw compressor according to
claim 1, includes: a casing that forms an outer shell of the screw compressor; a screw shaft provided in the casing and configured to be rotated by driving; a screw rotor fixed to the screw shaft and having spiral tooth grooves formed in an outer circumferential surface of the screw rotor; a gate rotor having a plurality of gate-rotor teeth that fit in the spiral tooth grooves of the screw rotor, the gate rotor defining together with the casing and the screw rotor, a compression chamber; a slide valve provided in a slide groove formed in an inner cylindrical surface of the casing, and configured to be slidable in a direction along a rotation axis of the screw rotor; and a bearing housing including an internal bearing that supports one end portion of the screw shaft in such a manner as to allow the end portion of the screw shaft to be rotated. The slide valve includes a valve body and a guide, connected to each other by a connection portion, the valve body being located on one side of the slide valve in a slide direction of the slide valve and facing the screw rotor, the guide being located on an other side of the slide valve in the slide direction of the slide valve and having a slide surface that faces an outer circumferential surface of the bearing housing. A raised surface portion is formed at an outer circumferential surface of the bearing housing and protrudes toward the slide surface of the guide of the slide valve. Advantageous Effects of Invention - In the screw compressor according to the present invention, the raised surface portion comes into contact with and supports the slide valve that has a valve body, which would tilt toward the screw rotor or rotate in a circumferential direction if the raised surface portion were not provided. It is therefore possible to prevent the slide valve from coming into contact with the screw rotor, and to hence provide a screw compressor having a high reliability.
-
- [
Fig. 1] Fig. 1 is a sectional view illustrating an internal configuration of a screw compressor according to an embodiment of the present invention. - [
Fig. 2] Fig. 2 is an enlarged sectional view of related portions that is taken along line A-A indicated by arrows inFig. 1 . - [
Fig. 3] Fig. 3 is an enlarged sectional view of the related portions that is taken along line B-B indicated by arrows inFig. 1 . - [
Fig. 4] Fig. 4 is a perspective view of a bearing housing of the screw compressor according to the embodiment of the present invention. - [
Fig. 5] Fig. 5 is an explanatory diagram of a suction step during an operation of the compression unit of the screw compressor according to the embodiment of the present invention. - [
Fig. 6] Fig. 6 is an explanatory diagram of a compression step during the operation of the compression unit of the screw compressor according to the embodiment of the present invention. - [
Fig. 7] Fig. 7 is an explanatory diagram of a discharge step during the operation of the compression unit of the screw compressor according to the embodiment of the present invention. - Hereinafter, an embodiment of the present invention will be described with reference to the figures. In each of the figures, components and portions that are the same as or equivalent to those of a previous figure are denoted by the same reference signs, and their descriptions will be omitted or simplified as appropriate. Furthermore, the shapes, sizes, and locations of the components and portions as illustrated in the figures can be changed appropriately within the scope of the present invention.
-
Fig. 1 is a sectional view illustrating an internal configuration of a screw compressor according to an embodiment of the present invention.Fig. 2 is an enlarged sectional view of related portions that is taken along line A-A indicated by arrows inFig. 1 .Fig. 3 is an enlarged sectional view of the related portions that is taken along line B-B indicated by arrows inFig. 1 .Fig. 4 is a perspective view of a bearing housing of the screw compressor according to the embodiment of the present invention. - A
screw compressor 100 according to the embodiment will be described by referring to by way of example the case where thescrew compressor 100 is a single-stage single-screw compressor. As illustrated inFig. 1 , thescrew compressor 100 includes acasing 1, acompression unit 2, and adriving unit 3. Thecasing 1 is cylindrical and forms an outer shell of thescrew compressor 100. Thecompression unit 2 and thedriving unit 3 are provided in thecasing 1. The interior of thecasing 1 is divided into a low-pressure space 10 and a high-pressure space 11. - As illustrated in
Fig. 1 , thecompression unit 2 includes ascrew shaft 4, ascrew rotor 5, a pair ofgate rotors 6, gate-rotor supports (not illustrated), a pair ofslide valves 7, and abearing housing 8. Thescrew rotor 5 is fixed to thescrew shaft 4. The bearinghousing 8 includes abearing 80 that supports an end portion of thescrew shaft 4 to allow the end portion to be rotated. - The
screw shaft 4 is provided in thecasing 1 and can be driven to rotate by the drivingunit 3. Thescrew shaft 4 extends in a direction along a tube axis of thecasing 1. One of end portions of thescrew shaft 4 is supported by thebearing 80, which faces the discharge side of thescrew rotor 5, such that the above one end portion can be rotated, and the other end portion is joined to thedriving unit 3. - As illustrated in
Figs. 1 and 2 , thescrew rotor 5 hasspiral tooth grooves 5a formed in an outer circumferential surface of a cylinder. Thescrew rotor 5 is fixed to thescrew shaft 4 and can be rotated together with thescrew shaft 4 by the drivingunit 3. In a direction along a rotation axis of thescrew rotor 5, a side of thescrew rotor 5 that adjoins the low-pressure space 10 is a refrigerant-suction side for refrigerant, and an end of thescrew rotor 5 that adjoins the high-pressure space 11 is a refrigerant-discharge side for the refrigerant. In addition, a predetermined space S is provided between thescrew rotor 5 and each of theslide valves 7. This is intended to avoid occurrence of, for example, seizure, by preventing theslide valve 7 and thescrew rotor 5 from contacting each other, for example, when thescrew compressor 100 is assembled or during an operation of thescrew compressor 100. - In the
gate rotors 6, gate-rotor teeth 6a are formed at outer peripheral portions of thegate rotors 6, and mesh with and fit in thetooth grooves 5a of thescrew rotor 5. As illustrated inFig. 1 , the pair ofgate rotors 6 are located to hold thescrew rotor 5 in a radial direction. In thecompression unit 2, thetooth grooves 5a of thescrew rotor 5 and the gate-rotor teeth 6a of thegate rotor 6 mesh with each other, thereby formingcompression chambers 20. To be more specific, in thescrew compressor 100, the twogate rotors 6 are provided on opposite sides of thescrew rotor 5, that is, thegate rotors 6 are displaced from each other by180 degrees. Thus, the number of theabove compression chambers 20 is two, and one of thecompression chambers 20 is located on an upper side of thescrew shaft 4, and the other is located on a lower side of thescrew shaft 4. The gate-rotor supports (not illustrated) have gate-rotor-support teeth that are located to face the gate-rotor teeth 6a, and support thegate rotors 6. - As illustrated in
Fig. 1 , each of theslide valves 7 is provided in aslide groove 12 formed in the inner cylindrical surface of thecasing 1 and is slidable in the direction along the rotation axis of thescrew rotor 5. Theslide valve 7 is, for example, an internal-volume-ratio regulating valve. Theslide valve 7 includes avalve body 70 and aguide 71. Thevalve body 70 is located to face thescrew rotor 5, and theguide 71 has a slide surface that faces an outer circumferential surface of the bearinghousing 8. Thevalve body 70 and theguide 71 are connected to each other by aconnection portion 72. Between thevalve body 70 and theguide 71, adischarge port 7a is provided to allow refrigerant compressed in thecompression chamber 20 to be discharged from thedischarge port 7a. The refrigerant discharged from thedischarge port 7a is discharged into the high-pressure space (not illustrated) through a discharge gas passage. - The
slide valve 7 is connected to a slide-valve driving device 74 by arod 73 fixed to the end face of theguide 71. When therod 73 is driven by the slide-valve driving device 74 to move in an axial direction of therod 73, theslide valve 7 is moved by therod 73 in parallel with thescrew shaft 4. The slide-valve driving device 74 is, for example, a device that is driven by a gas pressure, a device that is driven by an oil pressure, or a device that is driven by a motor. - In the
screw compressor 100, since thevalve body 70 of theslide valve 7 is moved in parallel with thescrew shaft 4, a discharge timing at which refrigerant sucked into thecompression chamber 20 is discharged is adjusted. To be more specific, when theslide valve 7 is slid toward the suction side to advance the opening timing of thedischarge port 7a, the discharge timing can be advanced, and when theslide valve 7 is slid toward the discharge side to delay the opening timing of thedischarge port 7a, the discharge timing can be delayed. When the discharge timing is advanced, thescrew compressor 100 is operated at a low internal volume ratio, and when the discharge timing is delayed, thescrew compressor 100 is operated at a high internal volume ratio. - As illustrated in
Fig. 1 , the bearinghousing 8 is provided close to an end portion of thescrew rotor 5 that is located on the discharge side. The outside diameter of the bearinghousing 8 is greater than the outside diameter of thescrew rotor 5. Furthermore, , since the bearinghousing 8 needs to be into a casing bore 13 that accommodate thescrew rotor 5, the outside diameter of the bearinghousing 8 is less than the inside diameter of the casing bore 13. It should be noted that the outside diameter of the bearinghousing 8 may be less than the outside diameter of thescrew rotor 5. - As illustrated in
Figs. 1 ,3, and 4 , two raisedsurface portions 81 and recessedsurface portions 82 are formed at the outer circumferential surface of the bearinghousing 8. The raisedsurface portions 81 protrude toward theguides 71 of theslide valves 7. The recessedsurface portions 82 are formed in the same circumferential direction as the raisedsurface portions 81. The raisedsurface portions 81 are located within the movable range of theslide valve 7. The outside diameter of the raisedsurface portions 81 is, for example, greater than or equal to the inside diameter of the casing bore 13 that accommodates thescrew rotor 5. On the other hand, the outside diameter of the recessedsurface portions 82 is, for example, less than the inside diameter of the casing bore 13. - It should be noted that it is hard to form a raised
surface portion 81 by processing only part of the outer circumferential surface of the bearinghousing 8 using a lathe machine. Thus, the bearinghousing 8 is formed in advance, by use of a casting mold, to have recessedsurface portions 82 at the outer circumferential portion of the bearinghousing 8, and raisedsurface portions 81 are then formed by cutting both sides of each of the recessedsurface portions 82 using a lathe machine in such a manner as to extend in the same circumferential direction as the recessedsurface portions 82. That is, the recessedsurface portions 82 are portions that are used to form the raisedsurface portions 81 using the lathe machine. It should be noted that the surfaces of the recessedsurface portions 82 are castingsurface portions 82a formed by the casting mold. Since the recessedsurface portions 82 are portions that do not particularly function in thescrew compressor 100, it is no problem to keep the surfaces of the recessedsurface portions 82 as the casting surfaces 82a. - The driving
unit 3 includes anelectric motor 30. Theelectric motor 30 includes a stator 31 and amotor rotor 32. The stator 31 is inscribed in thecasing 1, fixed to an inner surface of thecasing 1, and has space in the radial direction. Themotor rotor 32 is provided inward of the stator 31 such that themotor rotor 32 can be rotated. Themotor rotor 32 is connected to an end portion of thescrew shaft 4, and is located on the same axis as the screw rotor. In thescrew compressor 100, when theelectric motor 30 is driven to rotate thescrew shaft 4, thescrew rotor 5 is also rotated. It should be noted that theelectric motor 30 is driven such that the rotational speed of theelectric motor 30 can be changed by an inverter (not illustrated), and is thus driven to increase/decrease the rotational speed of thescrew shaft 4. - Next, the operation of the
screw compressor 100 according to the embodiment will be described with reference toFigs. 5 to 7. Fig. 5 is an explanatory diagram of a suction step during an operation of the compression unit of the screw compressor according to the embodiment of the present invention.Fig. 6 is an explanatory diagram of a compression step during the operation of the compression unit of the screw compressor according to the embodiment of the present invention.Fig. 7 is an explanatory diagram of a discharge step during the operation of the compression unit of the screw compressor according to the embodiment of the present invention. It should be noted that the steps will be described while paying attention to thecompression chamber 20 indicated by a dot hatch pattern in each ofFigs. 5 to 7 . - As illustrated in
Figs. 5 to 7 , in thescrew compressor 100, when thescrew rotor 5 is rotated along with thescrew shaft 4 by theelectric motor 30, the gate-rotor teeth 6a of thegate rotors 6 are moved relative to thetooth grooves 5a that define thecompression chamber 20 such that each of the gate-rotor teeth 6a successively fit in thetooth grooves 5a. Thus, in thecompression chamber 20, the cycle of the suction step (Fig. 5 ), the compression step (Fig. 6 ), and the discharge step (Fig. 7 ) is repeated. -
Fig. 5 illustrates the state of thecompression chamber 20 in the suction step. Thescrew rotor 5 is driven by theelectric motor 30 to rotate in a direction indicated by a solid arrow in the figure. As a result, the volume of thecompression chamber 20 is decreased as illustrated inFig. 6 . - When the
screw rotor 5 is further rotated, as illustrated inFig. 7 , thecompression chamber 20 communicates with thedischarge port 7a. As a result, high-pressure refrigerant gas obtained through compression in thecompression chamber 20 is discharged from thedischarge port 7a to the outside. Then, similar compression is performed behind thescrew rotor 5. - It should be noted that the bearing
housing 8 is designed to have an outside diameter less than the inside diameter of the casing bore 13, since the bearinghousing 8 needs to be accommodated in the bearinghousing 8. Meanwhile, in thescrew compressor 100, when the temperature of the refrigerant gas compressed in thecompression chamber 20 rises, thescrew rotor 5 may thermally expand, and as a result the space between the outer circumferential surface of thescrew rotor 5 and the inner cylindrical surface of thecasing 1 and the space between the outer circumferential surface of thescrew rotor 5 and each of theslide valves 7 may decrease. In addition, after the operation of thescrew compressor 100 is stopped, thescrew rotor 5 may rotate backward because of a pressure differential between high pressure and low pressure in thecasing 1. When thescrew rotor 5 rotates backward, for example, the internal pressure of thecompression chamber 20 changes, as a result of which thevalve body 70 of theslide valve 7 may tilt toward thescrew rotor 5 or rotate in the circumferential direction. Consequently, part of thevalve body 70 of theslide valve 7 may project from the inner circumferential surface of the casing bore 13 and come into contact with thescrew rotor 5, thus causing, for example, seizure. - In view of the above, the
screw compressor 100 according to the embodiment is formed to include: thecasing 1 that forms the outer shell of thescrew compressor 100; thescrew shaft 4 that is provided in thecasing 1 and rotated by driving; thescrew rotor 5 that is fixed to thescrew shaft 4 and has thespiral tooth grooves 5a formed in the outer circumferential surface of thescrew rotor 5; and thegate rotors 6 that have gate-rotor teeth 6a to be fitted in thespiral tooth grooves 5a, and that defines together with thecasing 1 and thescrew rotor 5, thecompression chamber 20. In addition, thescrew compressor 100 includes: theslide valves 7 that are provided in theslide groove 12 formed in the inner cylindrical surface of thecasing 1, and that are slidable in the direction along the rotation axis of thescrew rotor 5; and the bearinghousing 8 including theinternal bearing 80 that rotatably supports one end portion of thescrew shaft 4. The raisedsurface portions 81 are formed at the outer circumferential surface of the bearinghousing 8 and protrude toward the slide surfaces of theslide valves 7. Therefore, although in general, thevalve bodies 70 of theslide valves 7 may tilt toward thescrew rotor 5 or rotate in the circumferential direction, since in thescrew compressor 100 according to the embodiment, the raisedsurface portions 81 come into contact with and support theslide valves 7, it is possible to prevent theslide valves 7 from coming into contact with thescrew rotor 5. Accordingly, it is possible to provide a screw compressor having a high reliability. - Furthermore, in the
screw compressor 100 according to the embodiment, an outside diameter of the raisedsurface portions 81 is greater than or equal to the inside diameter of the casing bore 13 that accommodates thescrew rotor 5. Thus, theslide valves 7 can be reliably supported by the raisedsurface portions 81, and theslide valves 7 can be more reliably prevented from coming into contact with thescrew rotor 5. - In addition, at the outer circumferential surface of the bearing
housing 8 in thescrew compressor 100 according to the embodiment, the recessedsurface portions 82 are formed in the same circumferential direction as the raisedsurface portions 81. The outside diameter of the recessedsurface portions 82 is less than the inside diameter of the casing bore 13. Thus, since the recessedsurface portions 82 are formed at the outer circumferential surface of the bearinghousing 8 in advance by the casting mold, the raisedsurface portions 81 can be formed by the lathe machine. It is therefore possible to more easily manufacture the screw compressor, and improve the productivity. - In addition, in the
screw compressor 100 according to the embodiment, the surfaces of the recessedsurface portions 82 are the castingsurfaces 82a formed by the casting mold. That is, in the recessedsurface portion 82, which does not particularly function in the structure of thescrew compressor 100, the surfaces of the casting surfaces 82a are kept as the casting surfaces 82a. Thus, as additional processing does not need to be performed on the recessedsurface portions 82. It is therefore possible to reduce the manufacturing cost and improve the productivity. - Although the embodiment of the present invention is descried above, the above descriptions concerning the configurations according to the embodiment are not limiting. For example, the internal configuration of the
screw compressor 100 is not limited to that explained in the above descriptions, and thescrew compressor 100 may include other components. In the above description, thescrew compressor 100 is described as a single-stage single-screw compressor. However, this is an example; that is, thescrew compressor 100 may be a two-stage single-screw compressor. Furthermore, each of theslide valves 7 is not limited to an internal-volume-ratio regulating valve, and may be, for example, a valve configured to regulate a compression capacity. In addition, although the twogate rotors 6 are illustrated in the drawings, the number ofgate rotors 6 is not limited to two, and onegate rotor 6 may be provided. In short, without departing from the technical concept of the present invention, the subject matter of the present invention covers design changes and various applications normally implemented by a person with ordinary skill in the art, as long as they still fall within the scope of the present invention as defined by the appended claims. - 1 casing 2
compression unit 3driving unit 4screw shaft 5screw rotor 5a tooth groove 6gate rotor 6a gate-rotor tooth 7slide valve 7a discharge port 8 bearinghousing 10 low-pressure space 11 high-pressure space 12slide valve 13 casing bore 20compression chamber 30 electric motor 31stator 32motor rotor 70valve body 71guide 72connection portion 73rod 74 slide-valve driving device 80bearing 81 raisedsurface portion 82 recessedsurface portion 82a casting surface 100 screw compressor S space
Claims (4)
- A screw compressor (100) comprising:a casing (1) that forms an outer shell of the screw compressor (100);a screw shaft (4) provided in the casing (1) and configured to be rotated by driving;a screw rotor (5) fixed to the screw shaft (4) and having spiral tooth grooves (5a) formed in an outer circumferential surface of the screw rotor (5);a gate rotor (6) having a plurality of gate rotor teeth (6a) that fit in the spiral tooth grooves (5a) of the screw rotor (5), the gate rotor (6) defining together with the casing (1) and the screw rotor (5), a compression chamber (20);a slide valve (7) provided in a slide groove (12) formed in an inner cylindrical surface of the casing (1), and configured to be slidable in a direction along a rotation axis of the screw rotor (5); anda bearing housing (8) including an internal bearing that supports one end portion of the screw shaft (4) in such a manner as to allow the end portion of the screw shaft (4) to be rotated,wherein the slide valve (7) includes a valve body (70) and a guide (71), connected to each other by a connection portion (72), the valve body (70) being located on one side of the slide valve (7) in a slide direction of the slide valve (7) and facing the screw rotor (5), the guide (71) being located on an other side of the slide valve (7) in the slide direction of the slide valve (7) and having a slide surface that faces an outer circumferential surface of the bearing housing (8),characterized in that a raised surface portion (81) is formed at an outer circumferential surface of the bearing housing (8) and protrudes toward the slide surface of the guide (71) of the slide valve (7).
- The screw compressor (100) of claim 1, wherein an outside diameter of the raised surface portion (81) is greater than or equal to an inside diameter of a casing bore (13) that accommodates the screw rotor (5).
- The screw compressor (100) of claim 1 or 2, whereinat the outer circumferential surface of the bearing housing (8), a recessed surface portion (82) is formed in the same circumferential direction as the raised surface portion (81), andan outside diameter of the recessed surface portion (82) is less than an inside diameter of a casing bore (13).
- The screw compressor (100) of claim 3, wherein a surface of the recessed surface portion (82) is a casting surface (82a) formed by a casting mold.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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PCT/JP2018/031152 WO2020039548A1 (en) | 2018-08-23 | 2018-08-23 | Screw compressor |
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EP3842641A1 EP3842641A1 (en) | 2021-06-30 |
EP3842641A4 EP3842641A4 (en) | 2021-07-14 |
EP3842641B1 true EP3842641B1 (en) | 2023-11-22 |
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EP18930891.9A Active EP3842641B1 (en) | 2018-08-23 | 2018-08-23 | Screw compressor |
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WO (1) | WO2020039548A1 (en) |
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WO2022244219A1 (en) * | 2021-05-21 | 2022-11-24 | 三菱電機株式会社 | Screw compressor |
WO2024075275A1 (en) * | 2022-10-07 | 2024-04-11 | 三菱電機株式会社 | Screw compressor |
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US8366405B2 (en) * | 2007-12-17 | 2013-02-05 | Daikin Industries, Ltd. | Screw compressor with capacity control slide valve |
US8845311B2 (en) | 2007-12-28 | 2014-09-30 | Daikin Industries, Ltd. | Screw compressor with adjacent helical grooves selectively opening to first and second ports |
JP2013060877A (en) * | 2011-09-13 | 2013-04-04 | Daikin Industries Ltd | Screw compressor |
JP6342821B2 (en) * | 2015-01-14 | 2018-06-13 | 日立ジョンソンコントロールズ空調株式会社 | Screw fluid machinery |
JP6332336B2 (en) * | 2016-06-14 | 2018-05-30 | ダイキン工業株式会社 | Screw compressor |
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