EP3252310B1 - Compresseur à vis - Google Patents

Compresseur à vis Download PDF

Info

Publication number
EP3252310B1
EP3252310B1 EP15879918.9A EP15879918A EP3252310B1 EP 3252310 B1 EP3252310 B1 EP 3252310B1 EP 15879918 A EP15879918 A EP 15879918A EP 3252310 B1 EP3252310 B1 EP 3252310B1
Authority
EP
European Patent Office
Prior art keywords
oil
slide valve
back surface
gap
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.)
Active
Application number
EP15879918.9A
Other languages
German (de)
English (en)
Other versions
EP3252310A4 (fr
EP3252310A1 (fr
Inventor
Katsuya Maeda
Masaaki Kamikawa
Takeshi Ito
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP3252310A1 publication Critical patent/EP3252310A1/fr
Publication of EP3252310A4 publication Critical patent/EP3252310A4/fr
Application granted granted Critical
Publication of EP3252310B1 publication Critical patent/EP3252310B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/50—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
    • F04C18/52—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • 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
    • 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 particularly to a screw compressor including a slide valve.
  • Conventional screw compressors each include a casing body and a screw rotor rotatably hounded in a cylinder chamber formed inside the casing body.
  • a screw compressor further includes a slide valve that controls the operation capacity by allowing a part of refrigerant introduced into a compression chamber to be bypassed to a low-pressure space during a compression process (see Patent Literature 1, for example).
  • the slide valve is disposed on an outer circumference of the screw rotor, and is movable in the axial direction of the screw rotor.
  • the slide valve is provided on the outer circumference of the screw rotor to be movable in the axial direction of the screw rotor, and a gap opens up between a casing body side (hereinafter referred to as the back surface side) of the slide valve and a slide valve side of the casing body.
  • a screw rotor-side surface (hereinafter referred to as the inner circumferential surface) of the slide valve is normally disposed to be located outside in the radial direction of an inner circumferential surface of the cylinder chamber to prevent mutual contact between the slide valve and the screw rotor. Consequently, the gap between the inner circumferential surface of the slide valve and the outer circumferential surface of the screw rotor is greater than the gap between an inner circumferential surface of the cylinder and the outer circumferential surface of the screw rotor.
  • the back surface side and the inner circumferential surface side of the slide valve each have a structurally necessary gap, as described above. Through these gaps, more than a small amount of refrigerant inevitably leaks from a discharge pressure (high pressure) side to a suction pressure (low pressure) side, degrading performance.
  • a technique of eliminating or reducing the refrigerant leakage from the inner circumferential surface of the slide valve includes a covering member provided to the inner circumferential surface of the slide valve to fill the gap between the inner circumferential surface of the slide valve and the outer circumferential surface of the screw rotor (see Patent Literature 2, for example).
  • US3314597A relates to a screw compressor which comprises a casing provided with a Working space comprising two intersecting cylindrical 'bores with parallel axes located between a low pressure and a high pressure end wall enclosing two cooperating rotors provided with helical lands and intervening grooves having a wrap angle of less than 360, which rotors are sealingly surrounded by said bores.
  • DE102011051730A1 discloses a screw compressor housing having screw rotor bores, screw rotors, a drive for the screw rotors, and a slider in a slider receptacle for adjusting a volume ratio of the screw compressor and which extends in a direction towards the high-pressure outlet in a guide trough of the slider receptacle that is open towards the screw rotor bores and which is capable of being positioned in a first position and a second position, wherein the volume ratio of the screw compressor is greater in one of the positions than in the other of the positions, the slider connected to a first cylinder element and cooperates with a second cylinder element, the cylinder elements being at least partially arranged in the insertion space and arranged following the slider in the displacement direction thereof on a side of the slider that is opposite the high-pressure outlet.
  • Patent Literature 2 With the covering member provided to the inner circumferential surface of the slide valve, the technique of Patent Literature 2 described above eliminates or reduces the gap between the inner circumferential surface of the slide valve and the outer circumferential surface of the screw rotor, thereby eliminating or reducing the refrigerant leakage from the inner circumferential surface side of the slide valve, as described above.
  • the technique of Patent Literature 2 does not eliminate or reduce the refrigerant leakage from the gap on the back surface side of the slide valve.
  • the casing body is formed with a partition wall that separates the discharge pressure (high pressure) side and the suction pressure (low pressure) side from each other (hereinafter referred to as the high-low pressure partition wall), and an inner circumferential side of the high-low pressure partition wall faces the back surface side of the slide valve. Further, a gap is opened up between the back surface of the slide valve and an inner circumferential surface of the high-low pressure partition wall to prevent mutual contact with each other. From this gap, the refrigerant leaks owing to the pressure difference between the discharge pressure (high pressure) and the suction pressure (low pressure) at a boundary of the high-low pressure partition wall. The pressure difference tends to be increased particularly in high-pressure refrigerant, such as R410A, substantially degrading performance due to the refrigerant leakage from the back surface side of the slide valve.
  • high-pressure partition wall that separates the discharge pressure (high pressure) side and the suction pressure (low pressure) side from each other
  • the present invention has been made to solve the above-described problems, and aims to provide a highly efficient screw compressor that eliminates or reduces the refrigerant leakage from the gap between the back surface of the slide valve and the inner circumferential surface of the high-low pressure partition wall.
  • a screw compressor according to the invention is defined by the independent claim of the application.
  • a screw compressor according to an embodiment of the present invention includes a casing body, a screw rotor disposed to rotate inside the casing body, a slide valve movably provided between the casing body and the screw rotor, a partition wall provided to face a back surface side of the slide valve and configured to divide an interior of the casing body into a discharge pressure space and a suction pressure space, and an injection mechanism configured to supply oil to a gap between an inner circumferential surface of the partition wall and the back surface side of the slide valve to seal the gap.
  • An embodiment of the present invention eliminates or reduces the refrigerant leakage from the gap between the back surface of the slide valve and the inner circumferential surface of the high-low pressure partition wall, and improves the performance of the screw compressor.
  • Embodiments 2, 4 and 5 are not according to the invention and are present for illustration purposes only.
  • Embodiment 3 is according to the invention, while embodiment 1 does not comprise a first oil groove of the invention, and thus it does not fall within the scope of the claims but it is useful for understanding the invention.
  • Fig. 1 is a schematic configuration diagram of a refrigeration apparatus including a screw compressor according to Embodiment 1 of the present disclosure.
  • the refrigeration apparatus includes devices such as a screw compressor 1, a condenser 5, an expansion valve 6, and an evaporator 7.
  • the screw compressor 1 includes a compression unit 2, a motor 3 connected in series with the compression unit 2 to drive the compression unit 2, and an oil separator 4.
  • refrigerating machine oil hereinafter referred to as the oil
  • the oil separator 4 separates the refrigerant and the oil from each other.
  • the separated oil is returned to the compression unit 2 by the pressure difference.
  • Fig. 1 illustrates the specifications of the screw compressor 1 including the oil separator 4 inside the screw compressor 1, the oil separator 4 may be configured to be disposed separately outside the screw compressor 1.
  • Fig. 2 is a schematic configuration diagram of the screw compressor according to Embodiment 1 of the present disclosure.
  • the screw compressor includes a tubular casing body 8, a screw rotor 9 housed inside the casing body 8, and the motor 3 that drives the screw rotor 9 to rotate.
  • the motor 3 is formed of a stator 3a inscribed in and fixed to the casing body 8 and a motor rotor 3b disposed inside the stator 3a.
  • the screw rotor 9 and the motor rotor 3b are both disposed on the same axis and fixed to a screw shaft 10.
  • the screw rotor 9 has an outer circumferential surface formed with a plurality of helical grooves (screw grooves) 11a, and is coupled to and driven to rotate by the motor rotor 3b fixed to the screw shaft 10. Further, the space inside the screw grooves 11a is surrounded by an inner tubular surface of the casing body 8 and a pair of gate rotors (not illustrated) that are in meshing engagement with the screw grooves 11a, thereby forming a compression chamber 11. Further, the interior of the casing body 8 is divided into a discharge pressure side and a suction pressure side by a high-low pressure partition wall 17. The high-low pressure partition wall 17 is provided to the casing body 8 to face a casing body 8 side of a later-described slide valve 14. Further, the discharge pressure side of the casing body 8 is formed with a pair of discharge ports 13, which open to a discharge chamber 12.
  • the casing body 8 includes the slide valve 14.
  • the slide valve 14 is connected to a rod 15 of a driving device 16, and is movable in the axial direction of the screw rotor 9.
  • the slide valve 14, which forms a part of the discharge ports 13, is a mechanism that changes a discharge start (compression completion) position of high-pressure gas compressed in the compression chamber 11, thereby changing a discharge opening time and changing an internal volume ratio.
  • the internal volume ratio refers to the ratio between the volume of the compression chamber 11 at suction completion (compression start) time and the volume of the compression chamber 11 immediately before discharge.
  • two or more slide valves 14 may be provided, the illustration of the slide valves 14 other than one is omitted.
  • the casing body 8 side and a screw rotor 9 side of the slide valve 14 will be referred to as the "back surface side” and the “inner circumferential side,” respectively.
  • Fig. 3 is an illustrative diagram of an operation of the conventional screw compressor illustrated for comparison with an operation of Embodiment 1.
  • Fig. 4 is a diagram illustrating a refrigerant leakage passage of a conventional slide valve illustrated for comparison with the slide valve of Embodiment 1, with the slide valve viewed from a back surface side.
  • the conventional configuration allows a slide valve 140 provided inside a casing body 80 to move in the axial direction of a screw rotor 90.
  • a gap opens up between a back surface 140a of the slide valve 140 and an inner circumferential surface 170a of a high-low pressure partition wall 170, which is a part of the casing body 80.
  • the high-low pressure partition wall 170 is located at a position separating a discharge pressure (high pressure) side and a suction pressure (low pressure) side from each other. Consequently, refrigerant leaks from the gap, as indicated by an arrow in Fig. 3 , degrading performance.
  • Embodiment 1 on the other hand, has the following configuration.
  • Fig. 5 is an illustrative diagram of an operation of the screw compressor according to Embodiment 1 of the present disclosure.
  • Fig. 6 is a perspective view illustrating an oil passage of the slide valve of the screw compressor according to Embodiment 1 of the present disclosure, with the slide valve viewed from a back surface side of the slide valve.
  • the slide valve 14 of Embodiment 1 includes an injection mechanism 20 that injects the oil to a gap between sealing surfaces S, which define the gap between a back surface side 14f of the slide valve 14 and an inner circumferential surface 17a of the high-low pressure partition wall 17.
  • the injection mechanism 20 will be described in detail below.
  • Fig. 7 is a perspective view of the slide valve of the screw compressor according to Embodiment 1 of the present disclosure, with the slide valve viewed from an inner surface side of the slide valve.
  • Fig. 8 is a plan view of the slide valve of the screw compressor according to Embodiment 1 of the present disclosure, with the slide valve viewed from the back surface side of the slide valve.
  • Fig. 9 is a view of the slide valve in Fig. 6 , with the slide valve vertically reversed and viewed in the direction of arrow X (in a direction in which a sump 14m is visible).
  • Fig. 10 is a sectional view taken along line A-A in Fig. 9 .
  • Fig. 11 is a sectional view taken along line B-B in Fig. 9 .
  • arrows indicate oil passages.
  • the slide valve 14 includes a valve body 14a, a guide portion 14b, and a connecting portion 14c that connects the valve body 14a and the guide portion 14b.
  • a gap communicating with the discharge ports 13 is opened up between the valve body 14a and the guide portion 14b to form a part of the discharge ports 13.
  • a discharge port end portion 14d of an inner circumferential side 14e on a side of the discharge ports 13 forms a part of the discharge ports 13, and determines the time of discharging the compressed refrigerant.
  • the discharge port end portion 14d is moved in the axial direction of the screw rotor 9 at the same as the slide valve 14 is moved in the axial direction of the screw rotor 9, thereby changing the internal volume ratio.
  • the guide portion 14b has a connecting hole 15a, to which the rod 15 is connected, as illustrated in Fig. 2 .
  • the slide valve 14 of Embodiment 1 is formed with an oil feed hole 14g passing through the slide valve 14 to inject the high-pressure oil to the screw rotor 9.
  • a screw rotor portion oil supply port 14i serving as an oil inflow-side opening is located on the back surface side 14f of the slide valve 14, and a screw rotor portion oil feed port 14h serving as an oil outflow-side opening is located on the inner circumferential side 14e of the slide valve 14.
  • the hole shape and the number of the oil feed hole 14g are not limited.
  • the slide valve 14 of Embodiment 1 is formed with an oil feed hole 14j to inject the oil to the gap (between the sealing surfaces S) between the high-low pressure partition wall 17 and the back surface side 14f of the slide valve 14.
  • a slide valve back surface portion oil supply port 14l serving as an oil inflow-side opening of the oil feed hole 14j is located on the back surface side 14f of the slide valve 14.
  • a slide valve back surface portion oil feed port 14k serving as an oil outflow-side opening of the oil feed hole 14j is located in a portion, facing the high-low pressure partition wall 17, of the back surface side 14f of the slide valve 14, that is, within the range of the sealing surfaces S.
  • the hole shape and the number of the oil feed hole 14j are not limited.
  • the oil feed hole 14j corresponds to a first oil feed hole of the present invention.
  • the slide valve 14 is formed with the sump 14m recessed on the back surface side 14f. As illustrated in Fig. 9 , the screw rotor portion oil supply ports 14i and the slide valve back surface portion oil supply port 14l are located in the sump 14m.
  • the high-pressure oil is injected to a gap between the inner circumferential side 14e of the slide valve 14 and a portion facing the inner circumferential side 14e and a gap between the back surface side 14f of the slide valve 14 and a portion facing the back surface side 14f to eliminate or reduce the refrigerant leakage from the screw rotor 9 and prevent burning.
  • the high-pressure oil in the oil separator 4 is first supplied by the pressure difference to the sump 14m provided in the slide valve 14 via a flow passage (not illustrated) inside the casing body 8. Subsequently, the oil supplied to the sump 14m is caused by the pressure difference to flow into the oil feed hole 14g from the screw rotor portion oil supply port 14i provided inside the sump 14m, and passes through the oil feed hole 14g. Then, the high-pressure oil is injected to the screw rotor 9 from the screw rotor portion oil feed port 14h.
  • Embodiment 1 is characterized in that the high-pressure oil is injected to a gap between the sealing surfaces S from the back surface side 14f.
  • the above-described oil in the sump 14m distributed by the oil separator 4 is used.
  • the high-pressure oil in the sump 14m is caused by the pressure difference to flow into the oil feed hole 14j from the slide valve back surface portion oil supply port 14l provided inside the sump 14m, and passes through the oil feed hole 14j.
  • the oil is injected to the gap between the sealing surfaces S from the slide valve back surface portion oil feed port 14k.
  • the oil feed hole 14j formed in the slide valve 14 corresponds to a part of the injection mechanism 20 of the present invention.
  • Embodiment 1 the screw rotor portion oil supply ports 14i and the slide valve back surface portion oil supply port 14l are set to be located inside the same sump 14m, but are not necessarily required to have this configuration, and may be configured to be located in separate sumps 14m. Further, Embodiment 1 basically aims to reduce the refrigerant leakage on the back surface side of the slide valve 14, and the oil feed hole 14j is also applicable to the slide valve 14 not having the oil feed hole 14g. Further, the thickness of the high-low pressure partition wall 17 may be increased to cause an opening of the oil feed hole 14j to face the high-low pressure partition wall 17 even when the slide valve 14 is moved.
  • Embodiment 1 includes the injection mechanism 20 that injects the oil to the gap between the sealing surfaces S to seal the sealing surfaces S, thereby eliminating or reducing the refrigerant leakage from the discharge pressure (high pressure) side to the suction pressure (low pressure) side. Consequently, the efficiency of the screw compressor 1 can be improved to contribute to energy saving.
  • the injection mechanism 20 is configured to have the oil feed hole 14j passing through the slide valve 14 to supply the oil flowing from the slide valve back surface portion oil supply port 14l of the oil feed hole 14j to the gap between the sealing surfaces S from the slide valve back surface portion oil feed port 14k, that is, simply configured to have a hole formed through the slide valve 14. Consequently, the injection mechanism 20 can be configured at low cost.
  • Embodiment 2 is different from Embodiment 1 only in the area having the oil feed hole for feeding the oil to the gap between the sealing surfaces S.
  • Fig. 12 is a schematic diagram illustrating main parts of a screw compressor according to Embodiment 2 of the present disclosure.
  • Fig. 13 is a perspective view of a slide valve of the screw compressor according to Embodiment 2 of the present disclosure, with the slide valve viewed from a backside of the slide valve.
  • Embodiment 2 differences from Embodiment 1 will be described, and configurations not described in Embodiment 2 are similar to those of Embodiment 1.
  • Embodiment 2 the oil feed hole 14j formed in the slide valve 14 in Embodiment 1 is eliminated, and an oil feed hole 17b is formed in the high-low pressure partition wall 17, which forms a part of the casing body 8. Further, a configuration is designed in which the inner circumferential surface 17a of the high-low pressure partition wall 17 has a slide valve back surface portion oil feed port 17c serving as an oil outflow-side opening of the oil feed hole 17b, to inject the high-pressure oil flowing into the oil feed hole 17b to the gap between the sealing surfaces S from the slide valve back surface portion oil feed port 17c.
  • the position of an oil inflow-side opening of the oil feed hole 17b is not particularly limited as long as the oil inflow-side opening of the oil feed hole 17b is formed at a position at which the oil inflow-side opening is capable of receiving the oil in the screw compressor 1. Further, the hole shape and the number of the oil feed hole 17b are not limited.
  • the oil feed hole 17b corresponds to a second oil feed hole of the present invention.
  • the high-pressure oil is injected to the gap between the sealing surfaces S from the slide valve back surface portion oil feed port 17c provided in the inner circumferential surface 17a of the high-low pressure partition wall 17. Consequently, the refrigerant leakage from the discharge pressure (high pressure) side to the suction pressure (low pressure) side in the sealing surfaces S can be eliminated or reduced, and the efficiency of the screw compressor 1 can be improved.
  • Embodiment 3 is different from Embodiment 1 only in that an oil groove is provided in the back surface side 14f of the slide valve 14.
  • Fig. 14 is a perspective view of a slide valve of a screw compressor according to Embodiment 3 of the present invention.
  • Embodiment 3 differences from Embodiment 1 will be described, and configurations not described in Embodiment 3 are similar to those of Embodiment 1.
  • the back surface side 14f of the valve body 14a of the slide valve 14 is formed with an oil groove 18 extending in the circumferential direction of the back surface side 14f to efficiently spread the oil injected to the gap between the sealing surfaces S in Embodiment 1 over the sealing surfaces S.
  • the position of processing the oil groove 18 is set to correspond within the range of the sealing surfaces S.
  • the oil groove 18 corresponds to a first oil groove of the present invention.
  • the sectional shape and the number of the above-described oil groove 18 are not limited.
  • Fig. 15 is an illustrative diagram of the positional relationship between the high-low pressure partition wall and the screw grooves corresponding to a stop position of the slide valve of the screw compressor according to Embodiment 3 of the present invention.
  • the oil groove 18 may extend across more than one of the screw grooves 11a, depending on a sliding position of the slide valve 14. The pressures in the screw grooves 11a are different from each other.
  • the oil groove 18 may allow communication between a high pressure-side screw groove 11a and a low pressure-side screw groove 11a and cause refrigerant leakage from the high-pressure side to the low-pressure side.
  • the oil groove 18 is not limited to the configuration in which the oil groove 18 is provided over the entirety in the circumferential direction of the back surface side 14f of the slide valve 14, and an area not processed to form a groove may be left in the back surface side 14f.
  • the area having the oil groove 18 is not limited to the back surface side 14f of the slide valve 14, and may be the inner circumferential surface 17a of the high-low pressure partition wall 17 forming a part of the sealing surfaces S, or may be both the back surface side 14f and the inner circumferential surface 17a.
  • the oil groove is formed to extend in the circumferential direction of the inner circumferential surface 17a similarly to the oil groove 18.
  • the oil groove thus provided in the inner circumferential surface 17a of the high-low pressure partition wall 17 corresponds to a third oil groove of the present invention.
  • Embodiment 3 effects similar to those of Embodiment 1 are obtained, and the following effects are obtained. That is, the oil injected to the gap between the sealing surfaces S from the back surface side 14f of the slide valve 14 is more likely to spread over the entire circumference of the back surface of the slide valve through the oil groove 18. With the oil groove 18, Embodiment 3 is more capable of eliminating or reducing the refrigerant leakage from the discharge pressure (high pressure) side to the suction pressure (low pressure) side in the sealing surfaces S than in a case in which the configuration of Embodiment 1 (the configuration having the slide valve back surface portion oil feed port 14k) is implemented alone. Consequently, the efficiency of the screw compressor 1 can be further improved.
  • Embodiment 4 corresponds to a configuration combining the configuration of Embodiment 2 and the configuration of Embodiment 3. That is, the oil groove 18 is provided to the slide valve 14 of the screw compressor 1 of Embodiment 2, which is characterized in that the oil is injected to the gap between the sealing surfaces S from the side of the high-low pressure partition wall 17.
  • Features such as the shape of the oil groove 18 and the position at which the oil groove 18 is formed are similar to those of Embodiment 3.
  • Fig. 16 is a perspective view of a slide valve of a screw compressor according to Embodiment 4 of the present disclosure.
  • Embodiment 4 differences from Embodiment 2 will be described, and configurations not described in Embodiment 4 are similar to those of Embodiment 2.
  • the oil injected to the gap between the sealing surfaces S from the side of the high-low pressure partition wall 17, as indicated by a solid-white arrow in Fig. 16 flows along the oil groove 18, as indicated by solid arrows, and efficiently spreads over the sealing surfaces S.
  • Embodiment 4 effects similar to those of Embodiment 2 are obtained, and the following effects are obtained. That is, the oil injected to the gap between the sealing surfaces S from the side of the high-low pressure partition wall 17 is more likely to spread over the entire circumference of the back surface of the slide valve through the oil groove 18. With the action of the oil groove 18, Embodiment 4 is more capable of eliminating or reducing the refrigerant leakage from the discharge pressure (high pressure) side to the suction pressure (low pressure) side in the sealing surfaces S than in a case in which the configuration of Embodiment 2 (the configuration in which the oil is injected to the gap between the sealing surfaces S from the side of the high-low pressure partition wall 17) is implemented alone. Consequently, the efficiency of the screw compressor 1 can be further improved.
  • Embodiment 5 is characterized in allowing communication between the sump 14m and the oil groove 18.
  • Fig. 17 is a diagram illustrating a structure of a slide valve of a screw compressor according to Embodiment 5 of the present disclosure.
  • the slide valve 14 of Embodiment 1 illustrated in Fig. 9 described above is configured to cause the oil in the sump 14m to pass through the valve body 14a with the oil feed hole 14j to inject the oil to the gap between the sealing surfaces S from the slide valve back surface portion oil feed port 14k.
  • Embodiment 5 is configured to cause the oil to flow along the back surface side (the outer circumferential surface) of the slide valve 14 to inject the oil to the gap between the sealing surfaces S.
  • the oil feed hole 14j of Embodiment 1 is eliminated, and an oil groove 18a is provided to communicate with the sump 14m to inject the high-pressure oil in the sump 14m to the gap between the sealing surfaces S through the oil groove 18a.
  • the oil groove 18a of Embodiment 5 is different from the oil groove 18 of Embodiment 3 only in that the oil groove 18 communicates with the sump 14m, and is similar to the oil groove 18 of Embodiment 3 in the other features.
  • the oil groove 18a corresponds to a second oil groove of the present invention.
  • the high-pressure oil in the sump 14m can be caused to spread over the sealing surfaces S without the oil feed hole 14j as in Embodiments 1 to 4, which passes through the slide valve 14. Consequently, the refrigerant leakage can be eliminated or reduced and efficiency of the screw compressor 1 can be improved with a simpler configuration.
  • Embodiments 1 to 5 may be combined as appropriate.
  • Embodiment 1 and Embodiment 2 may be combined to inject the oil to the gap between the sealing surfaces S from both the back surface side 14f of the slide valve 14 and the inner circumferential surface 17a of the high-low pressure partition wall 17.
  • Embodiments 1 to 5 are applicable to any screw compressor including a mechanism that has a gap between the back surface side 14f of the slide valve 14 and the inner circumferential surface 17a of the high-low pressure partition wall 17.
  • the compressor may be a multi-stage compressor including two or more compression units 2.
  • the present invention is useful not only in a screw compressor of constant speed specifications but also in an inverter-driven screw compressor.
  • the slide valve 14 capable of changing the internal volume ratio.
  • the slide valve to which the present invention is applicable is not limited to the slide valve capable of changing the internal volume ratio.
  • the slide valve to which the present invention is applicable may be a volume-control slide valve allowing a part of the refrigerant gas to be bypassed to the suction side (low pressure), or may be an immovable slide valve fixed to the casing body 8.

Landscapes

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

Claims (6)

  1. Compresseur à vis comprenant :
    un corps de boîtier (8) ;
    un rotor à vis (9) disposé de façon à tourner à l'intérieur du corps de boîtier (8) ;
    une vanne à tiroir (14) disposée de façon mobile entre le corps de boîtier (8) et le rotor à vis (9) ;
    une paroi de séparation (17) disposée de façon à faire face à un côté surface arrière (14f) de la vanne à tiroir (14) et configurée pour diviser un intérieur du corps de boîtier (8) en un espace de pression d'évacuation et un espace de pression d'aspiration ; et
    un mécanisme d'injection (20) configuré pour distribuer de l'huile dans un espacement entre une surface circonférentielle interne (17a) de la paroi de séparation (17) et le côté surface arrière (14f) de la vanne à tiroir (14) pour sceller l'espacement,
    le mécanisme d'injection (20) étant configuré de façon à avoir au moins un premier trou d'alimentation d'huile (14j) formé pour traverser la vanne à tiroir (14) et au moins un orifice d'alimentation d'huile (14k) servant d'ouverture côté écoulement de sortie d'huile de l'au moins un premier trou d'alimentation d'huile (14j), une extrémité de l'au moins un premier trou d'alimentation d'huile (14j) faisant face à la paroi de séparation (17) et configurée pour distribuer l'huile vers l'espacement depuis l'ouverture,
    dans lequel le mécanisme d'injection (20) comporte en outre une première rainure de graissage (18) disposée dans le côté surface arrière (14f) de la vanne à tiroir (14) de façon à faire face à la paroi de séparation (17) et configurée pour distribuer l'huile distribuée dans l'espacement, la première rainure de graissage (18) et l'au moins un premier trou d'alimentation d'huile (14j) communiquant l'un avec l'autre par l'intermédiaire de l'au moins un orifice d'alimentation d'huile (14k) pour distribuer l'huile dans l'espacement depuis la première rainure de graissage (18),
    dans lequel la première rainure de graissage (18) s'étend dans une direction circonférentielle du côté surface arrière (14f).
  2. Compresseur à vis selon la revendication 1, dans lequel la vanne à tiroir (14) comporte un carter (14m) évidé sur le côté surface arrière (14f), et une autre extrémité de l'au moins un premier trou d'alimentation d'huile (14j) s'ouvre sur le carter (14m).
  3. Compresseur à vis selon la revendication 2, le carter (14m) et la première rainure de graissage (18) communiquant l'un avec l'autre pour distribuer l'huile dans le carter (14m) vers l'espacement depuis la première rainure de graissage (18).
  4. Compresseur à vis selon l'une quelconque des revendications 1 à 3, dans lequel le mécanisme d'injection (20) est configuré pour avoir au moins un deuxième trou d'alimentation d'huile (17b) formé dans la paroi de séparation (17), une extrémité de l'au moins un deuxième trou d'alimentation d'huile (17b) ouvrant sur la surface circonférentielle interne (17a) de la paroi de séparation (17) pour distribuer l'huile dans l'espacement.
  5. Compresseur à vis selon l'une quelconque des revendications 1 à 4, dans lequel le mécanisme d'injection (20) comporte en outre une troisième rainure de graissage disposée dans la surface circonférentielle interne (17a) de la paroi de séparation (17) et configurée pour distribuer l'huile distribuée dans l'espacement.
  6. Compresseur à vis selon la revendication 5, dans lequel la troisième rainure de graissage est disposée dans la surface circonférentielle interne (17a) de la paroi de séparation (17) et s'étend dans une direction circonférentielle de la surface circonférentielle interne (17a).
EP15879918.9A 2015-01-28 2015-01-28 Compresseur à vis Active EP3252310B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2015/052275 WO2016121021A1 (fr) 2015-01-28 2015-01-28 Compresseur à vis

Publications (3)

Publication Number Publication Date
EP3252310A1 EP3252310A1 (fr) 2017-12-06
EP3252310A4 EP3252310A4 (fr) 2018-10-10
EP3252310B1 true EP3252310B1 (fr) 2024-04-03

Family

ID=56542677

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15879918.9A Active EP3252310B1 (fr) 2015-01-28 2015-01-28 Compresseur à vis

Country Status (4)

Country Link
EP (1) EP3252310B1 (fr)
CN (1) CN207333184U (fr)
TW (1) TWI579464B (fr)
WO (1) WO2016121021A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7112031B2 (ja) * 2019-03-01 2022-08-03 三菱電機株式会社 スクリュー圧縮機
WO2021106061A1 (fr) * 2019-11-26 2021-06-03 三菱電機株式会社 Compresseur à vis

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NO117317B (fr) * 1964-03-20 1969-07-28 Svenska Rotor Maskiner Ab
DE1804884A1 (de) * 1968-10-24 1970-09-17 Gutehoffnungshuette Sterkrade Schraubenverdichter mit zwei ineinandergreifenden Schraubenrotoren und einem axialverstellbaren Steuerschieber zur Foerdermengenregelung und OEleinspritzung
JPS5147051Y2 (fr) * 1972-12-08 1976-11-13
JPS5147051U (fr) * 1974-10-05 1976-04-07
JPH05106572A (ja) * 1991-10-17 1993-04-27 Daikin Ind Ltd 一軸形スクリユー圧縮機
BR112013006770A2 (pt) * 2010-09-30 2020-12-15 Daikin Industries Ltd. Compressor de rosca
DE102011051730A1 (de) * 2011-07-11 2013-01-17 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter
JP5865056B2 (ja) * 2011-12-16 2016-02-17 三菱電機株式会社 スクリュー圧縮機

Also Published As

Publication number Publication date
EP3252310A4 (fr) 2018-10-10
EP3252310A1 (fr) 2017-12-06
TWI579464B (zh) 2017-04-21
CN207333184U (zh) 2018-05-08
TW201627577A (zh) 2016-08-01
WO2016121021A1 (fr) 2016-08-04

Similar Documents

Publication Publication Date Title
US9181945B2 (en) Scroll compressor with channels intermittently communicating internal and external compression chambers with back pressure chamber
US8337183B2 (en) Oil return valve for a scroll compressor
EP2505841B1 (fr) Compresseur à vis et unité de refroidisseur l'utilisant
EP1846642B1 (fr) Lubrification de compresseur a vis
EP3199814B1 (fr) Compresseur à vis et dispositif à cycle de réfrigération
US8622725B2 (en) Mechanical compression ratio changing screw compressor
CA2885727C (fr) Appareil et procede pour ameliorer le rendement de compresseur
TWI626380B (zh) 螺桿壓縮機以及具有螺桿壓縮機之冷凍循環裝置
CN107002679B (zh) 具有油关闭阀的螺杆压缩机和方法
EP3252310B1 (fr) Compresseur à vis
EP3133288B1 (fr) Compresseur à vis
US11174862B2 (en) Screw compressor
US11346221B2 (en) Backpressure passage rotary compressor
CN114599884B (zh) 供液式螺杆压缩机
JP7154773B2 (ja) スクロール流体機械
JP6881245B2 (ja) 圧縮機
EP4067659B1 (fr) Compresseur à vis
JP4421359B2 (ja) 気体圧縮機
US20190316587A1 (en) Motor-operated compressor
JP2006194193A (ja) スクロール式流体機械

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20170825

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20180912

RIC1 Information provided on ipc code assigned before grant

Ipc: F04C 29/00 20060101ALI20180906BHEP

Ipc: F04C 18/52 20060101ALI20180906BHEP

Ipc: F04C 18/16 20060101AFI20180906BHEP

Ipc: F04C 27/00 20060101ALI20180906BHEP

Ipc: F04C 28/12 20060101ALI20180906BHEP

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20211125

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20231204

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602015088197

Country of ref document: DE