EP3505765B1 - Compresseur à vis et dispositif à cycle frigorifique - Google Patents

Compresseur à vis et dispositif à cycle frigorifique Download PDF

Info

Publication number
EP3505765B1
EP3505765B1 EP16914144.7A EP16914144A EP3505765B1 EP 3505765 B1 EP3505765 B1 EP 3505765B1 EP 16914144 A EP16914144 A EP 16914144A EP 3505765 B1 EP3505765 B1 EP 3505765B1
Authority
EP
European Patent Office
Prior art keywords
screw
refrigerant
refrigerant liquid
slide valve
suction
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16914144.7A
Other languages
German (de)
English (en)
Other versions
EP3505765A4 (fr
EP3505765A1 (fr
Inventor
Katsuya Maeda
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 EP3505765A1 publication Critical patent/EP3505765A1/fr
Publication of EP3505765A4 publication Critical patent/EP3505765A4/fr
Application granted granted Critical
Publication of EP3505765B1 publication Critical patent/EP3505765B1/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
    • 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
    • F04C29/0014—Injection of a fluid in the working chamber for sealing, cooling and lubricating with control systems for the injection of the fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a

Definitions

  • the present invention relates to a screw compressor and a refrigeration cycle apparatus, which are to be used for, for example, compression of refrigerant for a refrigerating machine.
  • a single-screw compressor includes a screw rotor and two disc-shaped gate rotors, which are accommodated in a casing.
  • the screw rotor has a plurality of helical screw grooves formed in an outer peripheral surface.
  • the two disc-shaped gate rotors each have a plurality of teeth. Spaces surrounded by the casing, the screw grooves of the screw rotor, and the teeth of the gate rotors form compression chambers.
  • the teeth of the gate rotors move in the screw grooves of the screw rotor to repeat an operation of increasing and decreasing a capacity of each of the compression chambers.
  • a discharge temperature of discharge refrigerant gas discharged from the compressor increases under operating conditions at a large pressure difference between a high pressure and a low pressure or while a motor rotation speed is being increased by an inverter.
  • the discharge temperature is increased, there is a possibility that a trouble that the screw rotor may thermally expand to come into contact with the casing and is seized occurs.
  • Patent Literature 1 Japanese Unexamined Utility Model Application Publication No. Sho 63-130686
  • Patent Literature 2 JPS5738692A
  • a temperature of suction gas sucked into the compressor is lower than the temperature of the discharge gas. Therefore, during a steady operation, the screw rotor can be cooled by the suction of the suction gas into the screw grooves of the screw rotor.
  • the non-steady operation is an operation in which a degree of superheat of the suction gas (hereinafter referred to as "suction SH") rapidly rises or becomes higher than the suction SH given during the steady operation, for example, at start of the operation.
  • Patent Literature 1 describes that the oil separated by the oil separator is cooled and is injected into the compression chamber to decrease the discharge temperature.
  • a temperature rise of the oil during the non-steady operation has not been examined.
  • the discharge temperature rises, and therefore a temperature of the oil separated by the oil separator also inevitably increases.
  • the oil is supplied to the compression chamber while the temperature is kept high.
  • the temperature of the suction gas also increases during the non-steady operation. Therefore, the problem of seizing of the screw rotor still remains.
  • Patent Literature 2 discloses a screw compressor according to the preamble of claim 1.
  • the present invention has been attained to solve the problems described above, and an object thereof is to provide a screw compressor and a refrigeration cycle apparatus, which are capable of suppressing a rise in discharge temperature and suppressing seizing of a screw rotor during a non-steady operation.
  • a screw compressor including: a casing having a refrigerant liquid flow passage through which refrigerant liquid from an outside passes; a screw rotor having an outer peripheral surface with a plurality of screw grooves that form compression chambers and being arranged so as to be rotated inside the casing; and a slide valve provided between the casing and the screw rotor and configured to move slidably in a direction of a rotary shaft of the screw rotor, wherein the casing, the slide valve, or each of the casing and the slide valve has an oil injection port configured to supply oil to the plurality of screw grooves, and wherein the slide valve has a refrigerant liquid injection flow passage configured to bring the refrigerant liquid flow passage to communicate with any one of the plurality of screw grooves and configured to move between a first position of allowing the refrigerant liquid injection flow passage to communicate with one of the plurality of screw grooves from a time immediately before start of compression to a time immediately after the start
  • the refrigeration cycle apparatus includes a refrigerant circuit formed by sequentially connecting the screw compressor described above, a condenser, a main pressure-reducing device, and an evaporator.
  • the slide valve is located at the first position so that the liquid injection is started from the time immediately before the start of compression to the time immediately after the start of the compression. In this manner, the rise in discharge temperature can be suppressed. Further, the slide valve is located at the second position so that the liquid injection is performed at a position closer to the oil injection port than the first position in the direction of the rotary shaft. In this manner, the seizing of the screw rotor during the non-steady operation can be suppressed.
  • Fig. 1 is a refrigerant circuit diagram of a refrigeration cycle apparatus including a screw compressor according to Embodiment 1 of the present invention.
  • components denoted by the same reference symbols are the same or corresponding components, and this similarly applies to the entirety of the description. Further, forms of components given in the entirety of the description are merely examples, and are not limited to those given in the description.
  • a refrigeration cycle apparatus 100 includes a refrigerant circuit formed by sequentially connecting a screw compressor 102, a condenser 104, a main expansion valve 105, and an evaporator 106 by refrigerant pipes.
  • the refrigeration cycle apparatus 100 further includes a refrigerant liquid pipe 108.
  • the refrigerant liquid pipe 108 branches from a pipe between the condenser 104 and the main expansion valve 105, and is connected to the screw compressor 102.
  • a flow control valve 111 configured to control a flow rate through the refrigerant liquid pipe 108 is provided to the refrigerant liquid pipe 108.
  • the flow control valve 111 is formed of, for example, an electronic expansion valve.
  • the refrigeration cycle apparatus 100 further includes an oil separator 112 and an oil supply pipe 113.
  • the oil separator 112 is configured to separate oil from refrigerant discharged from the screw compressor 102.
  • the oil supply pipe 113 is configured to supply the oil separated by the oil separator 112 to the screw compressor 102. Description is given on the configuration in which the oil separator 112 is installed independently of the compressor. However, a configuration in which an oil separator is integrated with a compressor to thereby allowing the compressor to have functions of the oil separator may also be used.
  • the screw compressor 102 is configured to suck the refrigerant and compress the refrigerant into a high-temperature and high-pressure state.
  • the screw compressor 102 is driven by supply of power from a power supply source (not shown) to a motor 103 through an inverter 101.
  • the condenser 104 is configured to cool and condense discharge refrigerant gas from the screw compressor 102.
  • the main expansion valve 105 is configured to expand refrigerant liquid passing through a refrigerant liquid pipe 109, and includes an electronic expansion valve.
  • the main expansion valve 105 corresponds to a main pressure-reducing device according to the present invention. Besides the electronic expansion valve, devices in other forms such as a mechanical expansion valve, a thermal expansion valve, or a capillary tube may be used as the main pressure-reducing device as long as a similar role is fulfilled.
  • the evaporator 106 is configured to evaporate the refrigerant having flowed out from the main expansion valve 105.
  • a suction gas temperature sensor 120 configured to detect a temperature of suction gas sucked into the screw compressor 102 is provided on a suction side of the screw compressor 102. An inlet temperature detected by the suction gas temperature sensor is output to a controller 110 described later.
  • the refrigeration cycle apparatus 100 further includes the controller 110.
  • the controller 110 is configured to perform overall control of the refrigeration cycle apparatus 100 such as opening-degree control of the main expansion valve 105, position control of a slide valve described later, and opening-degree control of the flow control valve 111.
  • the controller 110 controls the main expansion valve 105 so that a suction SH takes a target value during a steady operation.
  • the steady operation means an operation other than a non-steady operation
  • the non-steady operation means an operation in which a degree of superheat of the suction gas (hereinafter referred to as "suction SH”) rapidly rises or becomes higher than the suction SH given during the steady operation, for example, at start of the operation.
  • suction SH a degree of superheat of the suction gas
  • the controller 110 controls the flow control valve 111 in accordance with a discharge temperature. Specifically, the controller 110 controls the flow control valve 111 so that the discharge temperature falls within a preset set range.
  • the controller 110 may include hardware such as a circuit device configured to achieve functions thereof, or may include a combination of a computing device such as a microcomputer or a CPU and software executed thereon.
  • the screw compressor 102 sucks and compresses the refrigerant gas being gaseous refrigerant, and thereafter discharges the refrigerant gas.
  • the discharge gas discharged from the screw compressor 102 flows into the oil separator 112.
  • the refrigerant and the oil mixed with the refrigerant are separated from each other.
  • the refrigerant is cooled in the condenser 104.
  • the refrigerant having been cooled in the condenser 104 is split after passing through the condenser 104. Main-flow refrigerant thereof is reduced in pressure and expanded by the main expansion valve 105.
  • the refrigerant having flowed out from the main expansion valve 105 is heated in the evaporator 106 to turn into refrigerant gas.
  • the refrigerant gas having flowed out from the evaporator 106 is sucked into the screw compressor 102.
  • refrigerant as part of refrigerant liquid having passed through the condenser 104 and is split from the main-flow refrigerant flows into the refrigerant liquid pipe 108.
  • the refrigerant liquid is injected into compression chambers 5 due to a differential pressure between a pressure of the refrigerant liquid in the refrigerant liquid pipe 108 and a pressure in the compression chamber of the screw compressor 102.
  • the injected refrigerant liquid is mixed with the refrigerant gas being currently compressed, is compressed, and is discharged from the screw compressor 102.
  • the oil discharged together with the refrigerant from the screw compressor 102 is separated from the refrigerant in the oil separator 112, and is returned to the screw compressor 102 through the oil supply pipe 113.
  • the action of returning the oil to the screw compressor 102 prevents the screw compressor 102 from running out of the oil.
  • Fig. 2 is a schematic configurational view of the screw compressor according to Embodiment 1 of the present invention.
  • Fig. 3 is a developed view of an outer peripheral surface of a screw rotor of the screw compressor according to Embodiment 1 of the present invention and is an illustration of a positional relationship between screw grooves and an injection port when the slide valve is arranged at a first position on a discharge side.
  • Fig. 1 is a schematic configurational view of the screw compressor according to Embodiment 1 of the present invention.
  • Fig. 3 is a developed view of an outer peripheral surface of a screw rotor of the screw compressor according to Embodiment 1 of the present invention and is an illustration of a positional relationship between screw grooves and an injection port when the slide valve is arranged at a first position on a discharge side.
  • FIG. 4 is a developed view of the outer peripheral surface of the screw rotor of the screw compressor according to Embodiment 1 of the present invention and is an illustration of a positional relationship between the screw grooves and the injection port when the slide valve is arranged at a second position on the suction side.
  • the screw compressor 102 includes a casing 1, a screw rotor 3, gate rotors 6, the motor 103 configured to drive the screw rotor 3 to rotate, a slide valve 7, and other components.
  • the casing 1 is configured to accommodate the screw rotor 3, the gate rotors 6, the motor 103, the slide valve 7, and other components.
  • the casing 1 has an accommodation wall 1a having a cylindrical shape, which internally defines an approximately cylindrical space. Inside the accommodation wall 1a, the screw rotor 3 having an approximately columnar shape is arranged.
  • the screw rotor 3 has one end being a suction side (right side of Fig. 2 ) for the refrigerant and the other end being a discharge side (left side of Fig. 2 ).
  • a plurality of helical screw grooves 3a are formed on an outer peripheral surface of the screw rotor 3.
  • a rotary shaft 4 is provided in a center of the screw rotor 3 so as to rotate integrally therewith.
  • the rotary shaft 4 is borne by a bearing 2, which is provided to the casing 1, so as to be freely rotatable.
  • the motor 3 having a frequency controlled by, for example, the invertor 101 is coupled to an end of the rotary shaft 4, which is on a side opposite to the bearing 2.
  • the motor 103 includes a stator 103a and a motor rotor 103b.
  • the stator 103a internally contact and fixed to the casing 1.
  • the motor rotor 103b is arranged inside the stator 103a.
  • the rotary shaft 4 is coupled to the motor rotor 103 so as to drive the screw rotor 3 to rotate.
  • Each of the gate rotors 6 has a disc-like shape and has an outer peripheral portion having a plurality of teeth 6a to be meshed with the screw grooves 3a. Spaces surrounded by the teeth 6a of the gate rotors 6, the screw grooves 3a, and the accommodation wall 1a of the casing 1 define the compression chambers 5.
  • the space inside the casing 1 is partitioned by a partition wall (not shown) into a low-pressure side into which low-pressure gas refrigerant is introduced from the evaporator 106 of the refrigerant circuit and a high-pressure side into which high-pressure gas refrigerant discharged from the compression chamber 5 flows.
  • a discharge port (see Figs. 5 referred to later) 10 which is open to a discharge chamber (not shown), is formed on the high-pressure side of the casing 1.
  • the casing 1 has an oil injection port 114 configured to supply the oil separated by the oil separator 112 to the screw grooves 3a.
  • the oil injection port 114 is formed at a position facing the screw groove 3a from a time immediately before start of the compression to a time immediately after the start of the compression, as illustrated in Fig. 3 and Fig. 4 .
  • the oil injection port 114 is formed in the casing 1.
  • the oil injection port 114 may be formed in a capacity-control slide valve or an internal capacity ratio variable slide valve described later. Further, the oil injection ports may be formed in both the casing and the capacity-control or internal capacity ratio variable slide valve described above.
  • a slide groove 1b extending in a direction of the rotary shaft 4 of the screw rotor 3 is formed.
  • the slide valve 7 for changing a liquid injection position is accommodated so as to be freely movable slidably in the direction of the rotary shaft 4.
  • the slide valve 7 closes openings of the screw grooves 3a to define the compression chambers 5, and therefore forms part of the inner peripheral surface 1aa together with the casing 1.
  • Fig. 2 illustrates a configuration in which the single slide valve 7 for changing a liquid injection position is provided in the casing 1.
  • the capacity control slide valve or the internal capacity ratio variable slide valve may be additionally provided.
  • illustration is given on an example in which an internal capacity ratio variable slide valve 11 is provided.
  • the slide valve 7 is configured to change an injection position for injection of the refrigerant liquid to the screw grooves 3a that define the compression chambers 5 and has a refrigerant liquid injection flow passage 7a, which is configured to inject the refrigerant liquid from an outside into the screw grooves 3a and is formed to pass therethrough.
  • the refrigerant liquid injection flow passage 7a has a liquid reservoir groove 7aa having an elongated groove shape and an injection port 7ab having a cylindrical shape.
  • the liquid reservoir groove 7aa is formed on a surface side of the slide valve 7 facing the accommodation wall 1a of the casing 1, and extends in a sliding direction.
  • the injection port 7ab is formed so as to communicate with the liquid reservoir groove 7aa, and is open to the screw rotor 3 side.
  • the slide valve 7 is configured to be movable between the first position (see Fig. 3 ) on the discharge side and the second position (see Fig. 4 ) on the suction side.
  • injection timing can be delayed.
  • the slide valve 7 moves to the second position on the suction side, the injection timing can be advanced.
  • the position of the injection port 7ab in a state in which the slide valve 7 is located at the first position is a position on the discharge side (left side of Fig. 3 ) along a suction side end surface 1d of the casing 1 on a plan view of the slide valve 7 and the casing 1 as viewed from an outer side, as illustrated in Fig. 3 . Therefore, from another point of view, the position of the injection port 7ab in the state in which the slide valve 7 is located at the first position can be described as a position facing the screw groove 3a from the time immediately before the start of compression to the time immediately after the start of compression. Therefore, under the state in which the slide valve 7 is located at the first position, the liquid injection of the refrigerant liquid to the screw grooves 3a is started between the time immediately before the start of compression and the time immediately after the start of compression.
  • the position of the injection port 7ab in a state in which the slide valve 7 is located at the second position on the suction side is a position facing a screw groove 3ab before the start of compression, specifically, in a suction stroke, as illustrated in Fig. 4 . Therefore, under the state in which the slide valve 7 is located at the second position, the refrigerant liquid is injected into the screw groove 3a before the start of compression.
  • the refrigerant liquid to the screw groove 3a in the suction stroke when the refrigerant liquid is injected at an early stage of the suction stroke, the suction of the suction gas into the compression chambers 5 is inhibited. Therefore, it is preferred that the injection of the refrigerant liquid to the screw groove 3a in the suction stroke be carried out in a later stage of the suction stroke.
  • the position of the injection port 7ab and the position of the oil injection port 114 in the state in which the slide valve 7 is located at the first position are each "the position facing the screw groove 3a from the time immediately before the start of compression to the time immediately after the start of compression", but are different in position in a circumferential direction.
  • the slide valve 7 is provided in a direction opposite to a rotating direction of the screw rotor 3 with respect to the oil injection port 114. Therefore, the injection port 7ab and the oil injection port 114 in the state in which the slide valve 7 is located at the first position are different in position in the direction of the rotary shaft 4 (position in a horizontal direction of Fig.
  • the slide valve 7 is connected to a drive device 9 such as a piston via a coupling rod 8 and is movable between the first position and the second position inside the slide groove 1b by drive of the driving device 9.
  • the drive device 9 may be driven by a gas pressure or a hydraulic pressure, and, besides the piston, may be a motor or other devices without limiting a driving method.
  • the casing 1 has a refrigerant liquid flow passage 1c, which brings the outside of the casing 1 to communicate with slide groove 1b, as illustrated in Fig. 2 .
  • a positional relationship between the refrigerant liquid flow passage 1c and the slide valve 7 is set so that an opening of the refrigerant liquid flow passage 1c on the slide groove 1b side communicates with the liquid reservoir groove 7aa formed on the side valve 7 regardless of whether the slide valve 7 is located at the first position or the second position.
  • the refrigerant liquid pipe 108 (see Fig. 1 ) is connected to an opening of the refrigerant liquid flow passage 1c on an outer side of the casing.
  • the refrigerant liquid split from the refrigerant liquid flowing between the condenser 104 and the main expansion valve 15 flows into the screw grooves 3a that define the compression chambers 5 through the refrigerant liquid pipe 108, the refrigerant liquid flow passage 1c, and the refrigerant liquid injection flow passage 7a.
  • the refrigerant used for the refrigerant circuit is not particularly limited.
  • an HFC-based refrigerant such as R134a, an HFO-based refrigerant being a low GWP refrigerant, or other refrigerants is used as the refrigerant.
  • Figs. 5 are illustrations of a mechanism of compression by the screw compressor according to Embodiment 1 of the present invention.
  • the screw rotor 3 is rotated by the motor 103 (see Fig. 2 ) via of the rotary shaft 4 (see Fig. 1 ).
  • the teeth 6a of the gate rotors 6 move relatively in the screw grooves 3a.
  • a portion surrounded by the dotted line in Figs. 5 represents the accommodation wall 1a of the casing 1.
  • the compression chambers 5 formed by the screw grooves 3a located in a region surrounded by the accommodation wall 1a are in the compression stroke. In this case, focusing on the compression chamber 5 which is indicated by the dot hatching in Figs. 5 , each of the strokes is described.
  • screw grooves 3ac and 3ad are in the compression stroke
  • screw grooves 3aa and 3ab are in the suction stroke
  • a screw groove 3ae is in the discharge stroke.
  • the screw rotor 3 in the state illustrated in Fig. 5(a) is driven by the motor 103 to rotate in the direction indicated by the solid arrow
  • the lower gate rotor 6 illustrated in Figs. 5 is rotated in a direction indicated by the outlined arrow along with the rotation of the screw rotor 3.
  • the upper gate rotor 6 illustrated in Figs. 5 is rotated in a direction opposite to the direction of rotation of the lower gate rotor 6, as indicated by the outlined arrow.
  • the compression chamber 5 has a maximized capacity, communicates with a low-pressure space in the casing 1, and is filled with the low-pressure refrigerant gas.
  • FIGs. 5 illustration of the slide groove 1b and the refrigerant liquid injection flow passage 7a of the slide valve 7 is omitted.
  • the refrigerant liquid flows into the screw groove 3a through the refrigerant liquid injection flow passage 7a to cool the refrigerant gas in the compression chamber 5, is compressed together with the suction gas in the compression stroke, and is discharged to the outside in the discharge stroke.
  • illustration of the oil injection port 114 is omitted.
  • the oil separated by the oil separator 112 is supplied from the oil injection port 114 to the screw groove 3a.
  • the injection of the refrigerant liquid for the purpose of suppressing increase in discharge temperature is performed.
  • the liquid injection during the steady operation is started in the compression chamber 5 from a time immediately before completion of the suction of the suction gas and a time immediately after the completion of the suction of the suction gas.
  • Embodiment 1 is characterized in that seizing of the screw rotor 3 during the non-steady operation is suppressed while the liquid injection is performed during the steady operation to suppress the increase in discharge temperature as described above.
  • the position of the liquid injection port and the position of the oil injection port 114 (positions in the horizontal direction in Fig. 3 and Fig. 4 ), which are close to each other in the direction of the rotary shaft 4, are effective.
  • a high-temperature oil separated by the oil separator 112 during the non-steady operation is supplied from the oil injection port 114 to the screw groove 3a.
  • the screw rotor 3 is rotating. Therefore, the oil is supplied to a circumferential region of the screw rotor 3, which includes a portion of the screw rotor 3 in the direction of the rotary shaft 4, in which the oil injection port 114 is located. Therefore, in particular, the circumferential region of the outer peripheral surface of the screw rotor 3 is liable to have an increased temperature and expand.
  • the portion having a high temperature can be cooled intensively to suppress thermal expansion of the screw rotor 3 so as to suppress the seizing of the screw rotor 3.
  • the position of the injection port 7ab in the direction of the rotary shaft 4 is only required to be set closer to the oil injection port 114.
  • the injection position during the steady operation and the injection position during the non-steady operation are required to be different from each other.
  • the different injection positions are achieved by movement of the slide valve 7. Specifically, the slide valve 7 moves to the first position on the discharge side during the steady operation, whereas the slide valve 7 moves to the second position on the suction side during the non-steady operation.
  • Whether a current operating state is a steady operation state or a non-steady operation state is determined based on the suction SH. Specifically, it is determined that the steady operation is being performed when the suction SH is low and that the non-steady operation is being performed when the suction SH is high.
  • Fig. 6 is a flowchart of the liquid injection control in the refrigeration cycle apparatus including the screw compressor according to Embodiment 1 of the present invention.
  • the flow control valve 111 is opened at an initial opening degree at the start of the operation.
  • the controller 110 calculates an actually measured suction SH based on the suction gas temperature detected by the suction gas temperature sensor 120. Then, when the actually measured suction SH is equal to or larger than a set suction SH_A and equal to or smaller than a set suction SH_B (Step S1; Yes), specifically, the current operating state is the steady operation state, the controller 110 moves the slide valve 7 to the first position on the discharge side as illustrated in Fig. 3 (Step S2).
  • the set suction SH_A and the set suction SH_B are preset in the controller 110.
  • the set suction SH_A and the set suction SH_B are threshold values for determining whether the operation is the steady operation or the non-steady operation.
  • the controller 110 controls the flow control valve 111 in accordance with an actually measured discharge temperature detected by a discharge temperature sensor (not shown). Specifically, when the actually measured discharge temperature is higher than a preset first temperature (Step S3; No), the opening degree of the flow control valve 111 is increased (Step S4). When the actually measured discharge temperature is lower than a second set temperature that is lower than the first set temperature (Step S5; No), the opening degree of the flow control valve 111 is decreased (Step S6). Meanwhile, when the actually measured discharge temperature is equal to or higher than the second set temperature and equal to or lower than the first set temperature (Step S3;Yes, Step S5; Yes), the current opening degree is maintained.
  • Step S8 when the determination in Step S1 is No and the actually measured suction SH is larger than the set suction SH_B (Step S7; Yes), specifically, the current operating state is the non-steady operation state, the controller 110 moves the slide valve 7 to the second position on the suction side as illustrated in Fig. 4 (Step S8). In this manner, as described above, the position of the injection port 7ab in the direction of the rotary shaft 4 can move closer to the oil injection port 114. Thus, the screw rotor 3 can be effectively cooled. Further, the liquid injection is performed for the screw groove 3ab before the start of the compression, specifically, the screw groove 3ab in the suction stroke and therefore contributes to a decrease in actually measured suction SH. As described above, when the liquid injection is performed for the screw groove 3ab in the suction stroke, the actually measured suction SH is gradually decreased.
  • Step S9 the opening degree of the main expansion valve 105 is increased.
  • Step S11 the opening degree of the flow control valve 111 is increased (Step S11).
  • Step S12 the opening degree of the flow control valve 111 is decreased (Step S12). Then, the processing returns to Step S1 to check a condition of decrease of the actually measured suction SH.
  • Step S1; No, Step S7; No When the actually measured suction SH is not equal to or higher than the set suction SH_A or equal to or smaller than the set suction SH_B and the actually measured suction SH is not larger than the set suction SH_B (Step S1; No, Step S7; No), specifically, when the actually measured SH is smaller than the set suction SH_A, it is determined that the liquid return operation (non-steady operation) is being performed.
  • the controller 110 moves the slide valve 7 to the first position on the discharge side (step S13) and subsequently decreases the opening degree of the main expansion valve 105 so as to increase the suction SH (Step S14).
  • a state is switched to a state in which the liquid injection is started from the time immediately before the start of compression and the time immediately after the start of compression. A subsequent operation is as described above.
  • the slide valve 7 having the injection port 7ab that moves in accordance with the suction SH is provided. Therefore, the injection position for the liquid injection can be changed for each of the steady operation and the non-steady operation.
  • the rise in discharge temperature can be suppressed without bringing about a defect that the liquid refrigerant leaks to the suction side to inhibit the suction of the suction gas refrigerant to the compression chamber 5.
  • the liquid injection can be performed for the circumferential region in which the thermal expansion is liable to occur due to the supply of oil from the oil injection port 114.
  • a quality defect such as seizing between the screw rotor 3 and the casing 1 can be suppressed.
  • the rise in suction SH can be suppressed by performing the liquid injection to the screw groove 3a in the suction stroke.
  • the flow rate of the liquid injection can be adjusted by the flow control valve 111 in accordance with the discharge temperature.
  • the rise in discharge temperature can be suppressed with an optimal liquid injection amount.
  • the inhibition of suction of the refrigerant into the compression chambers 5 can be minimized.
  • an influence on performance degradation can be reduced.
  • the configuration according to Embodiment 1 further includes an on-off valve 107 configured to open and close a flow passage of the refrigerant liquid pipe 108, which is provided to the refrigerant liquid pipe 108.
  • the on-off valve 107 includes, for example, a solenoid valve. Differences from Embodiment 1 are described in Embodiment 2, and a configuration that is not described in Embodiment 2 is similar to the configuration of Embodiment 1.
  • Fig. 7 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to Embodiment 2 of the present invention.
  • the refrigeration cycle apparatus 100 according to Embodiment 2 has a configuration in which the on-off valve 107 is additionally provided to the refrigerant liquid pipe 108 of Embodiment 1, which is illustrated in Fig. 1 .
  • the expansion valve serving as the flow control valve 111 is not generally guaranteed to completely close the flow passage. Therefore, when only the flow control valve 111 is provided to the refrigerant liquid pipe 108, the flow passage of the refrigerant liquid pipe 108 cannot be completely closed. Thus, even when the flow control valve 111 is closed in a case in which the liquid injection is not required to be performed, the liquid injection is slightly performed. Thus, when the on-off valve 107 is provided, the flow passage of the refrigerant liquid pipe 108 can be completely closed to stop the liquid injection.
  • Embodiment 2 the same effects as those obtained in Embodiment 1 are obtained.
  • the on-off valve 107 is provided to the refrigerant liquid pipe 108, and therefore Embodiment 2 additionally has the following effect. Specifically, in an operating region in which the discharge temperature is unlikely to increase, the liquid injection can be stopped by closing the on-off valve 107. Thus, performance deterioration due to a rise in intermediate pressure caused by the liquid injection performed at timing that is originally unnecessary can be prevented.
  • the screw compressor 102 is the single-screw compressor in Embodiment 1 and Embodiment 2.
  • the present invention is applicable to other screw compressors, for example, a twin-screw compressor. Further, the present invention is applicable to specifications with an economizer as the configuration of the refrigeration cycle.

Landscapes

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

Claims (8)

  1. Compresseur à vis (102), comprenant :
    un carter (1) comportant un passage d'écoulement de liquide réfrigérant (1c) à travers lequel passe un liquide réfrigérant provenant de l'extérieur ;
    un rotor à vis (3) comportant une surface périphérique externe dotée d'une pluralité de rainures à vis (3a) qui forment des chambres de compression (5) et agencé de sorte à tourner à l'intérieur du carter (1) ; et
    un tiroir (7) prévu entre le carter (1) et le rotor à vis (3) et configuré pour se déplacer de façon coulissante dans une direction d'un arbre rotatif (4) du rotor à vis (3),
    dans lequel le carter (1), le tiroir (7) ou chacun du carter (1) et du tiroir (7) comporte un orifice d'injection d'huile (114) configuré pour fournir de l'huile à la pluralité de rainures à vis (3a), et
    caractérisé en ce que
    le tiroir (7) comporte un passage d'écoulement d'injection de liquide réfrigérant (7a) configuré pour amener le passage d'écoulement de liquide réfrigérant (1c) à communiquer avec l'une quelconque de la pluralité de rainures à vis (3a) et est configuré pour se déplacer entre une première position autorisant le passage d'écoulement d'injection de liquide réfrigérant (7a) à communiquer avec l'une de la pluralité de rainures à vis (3a) d'un instant qui précède immédiatement le début d'une compression à un instant qui suit immédiatement le début de la compression et une seconde position autorisant le passage d'écoulement d'injection de liquide réfrigérant (7a) à communiquer avec une autre de la pluralité de rainures à vis (3a) qui se trouve dans une course d'aspiration avant le début de la compression et qui est plus proche de l'orifice d'injection d'huile (114) dans la direction de l'arbre rotatif (4) que la première position.
  2. Compresseur à vis (102) selon la revendication 1, dans lequel une position du tiroir (7) bascule vers la première position ou la seconde position en fonction d'un degré de surchauffe d'aspiration d'un gaz d'aspiration.
  3. Compresseur à vis (102) selon les revendications 1 ou 2, dans lequel le passage d'écoulement d'injection de liquide réfrigérant (7a) comporte une rainure réservoir de liquide (7aa) communiquant avec le passage d'écoulement de liquide réfrigérant (1c) indépendamment du fait que le tiroir (7) se trouve dans la première position ou dans la seconde position, et un orifice d'injection (7ab) communiquant avec la rainure réservoir de liquide (7aa).
  4. Appareil à cycle de réfrigération (100), comprenant un circuit de réfrigérant formé en raccordant séquentiellement le compresseur à vis (102) selon l'une quelconque des revendications 1 à 3, un condenseur (104), un dispositif de détente principal (105) et un évaporateur (106).
  5. Appareil à cycle de réfrigération (100) selon la revendication 4, comprenant en outre :
    un tuyau de liquide réfrigérant (108) ramifié à partir d'un tuyau entre le condenseur (104) et le dispositif de détente principal (105) et étant raccordé au passage d'écoulement de liquide réfrigérant (1c) du compresseur à vis (102) ;
    une soupape de régulation de débit (111) prévue sur le tuyau de liquide réfrigérant (108) et configurée pour réguler un débit du réfrigérant circulant dans le tuyau de liquide réfrigérant (108) ;
    un séparateur d'huile (112) configuré pour séparer l'huile du réfrigérant refoulé par le compresseur à vis (102) ;
    un tuyau d'alimentation en huile (113) configuré pour fournir l'huile séparée par le séparateur d'huile (112) à l'orifice d'injection d'huile (7ab) du compresseur à vis (102) ; et
    un dispositif de commande (110) configuré pour déplacer le tiroir (7) vers la première position ou la seconde position en fonction d'un degré de surchauffe d'aspiration du réfrigérant aspiré dans le compresseur à vis (102).
  6. Appareil à cycle de réfrigération (100) selon la revendication 5, dans lequel le dispositif de commande (110) déplace le tiroir (7) vers la première position lorsque le degré de surchauffe d'aspiration est égal ou inférieur à un degré de surchauffe d'aspiration prédéfini, et déplace le tiroir (7) vers la seconde position lorsque le degré de surchauffe d'aspiration est supérieur au degré de surchauffe d'aspiration prédéfini.
  7. Appareil à cycle de réfrigération (100) selon les revendications 5 ou 6, dans lequel le dispositif de commande (110) est configuré pour commander la soupape de régulation de débit (111) de sorte qu'une température de refoulement du réfrigérant refoulé par le compresseur à vis (102) se situe dans une plage prédéfinie.
  8. Appareil à cycle de réfrigération (100) selon l'une quelconque des revendications 5 à 7, comprenant en outre une soupape de commande (107) configurée pour ouvrir et fermer un passage d'écoulement du tuyau de liquide réfrigérant (108).
EP16914144.7A 2016-08-23 2016-08-23 Compresseur à vis et dispositif à cycle frigorifique Active EP3505765B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2016/074443 WO2018037469A1 (fr) 2016-08-23 2016-08-23 Compresseur à vis et dispositif à cycle frigorifique

Publications (3)

Publication Number Publication Date
EP3505765A1 EP3505765A1 (fr) 2019-07-03
EP3505765A4 EP3505765A4 (fr) 2019-08-14
EP3505765B1 true EP3505765B1 (fr) 2020-04-29

Family

ID=61246500

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16914144.7A Active EP3505765B1 (fr) 2016-08-23 2016-08-23 Compresseur à vis et dispositif à cycle frigorifique

Country Status (3)

Country Link
EP (1) EP3505765B1 (fr)
CN (1) CN109642579B (fr)
WO (1) WO2018037469A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK3660314T3 (da) 2018-10-09 2022-03-28 Maekawa Seisakusho Kk Skruekompressor og køleindretning
CN114729639A (zh) * 2019-11-26 2022-07-08 三菱电机株式会社 螺杆式压缩机

Family Cites Families (12)

* 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
JPS5091108U (fr) * 1973-12-19 1975-08-01
JPS5738692A (en) * 1980-08-20 1982-03-03 Ebara Corp Oil returning device of refrigerator
JPS56118988U (fr) * 1981-01-21 1981-09-10
JPS6332949Y2 (fr) * 1981-05-28 1988-09-02
EP1567770B1 (fr) * 2002-12-03 2017-01-18 BITZER Kühlmaschinenbau GmbH Compresseur a vis
JP4183021B1 (ja) * 2007-06-11 2008-11-19 ダイキン工業株式会社 圧縮機および冷凍装置
WO2010106787A1 (fr) * 2009-03-16 2010-09-23 ダイキン工業株式会社 Compresseur à vis
JP2012097645A (ja) * 2010-11-01 2012-05-24 Daikin Industries Ltd 圧縮機
WO2015114851A1 (fr) * 2014-01-29 2015-08-06 三菱電機株式会社 Compresseur à vis
EP3199814B1 (fr) * 2014-09-24 2021-01-06 Mitsubishi Electric Corporation Compresseur à vis et dispositif à cycle de réfrigération
WO2016084176A1 (fr) * 2014-11-26 2016-06-02 三菱電機株式会社 Compresseur à vis et dispositif à cycle de réfrigération

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP3505765A4 (fr) 2019-08-14
WO2018037469A1 (fr) 2018-03-01
EP3505765A1 (fr) 2019-07-03
CN109642579B (zh) 2020-12-01
CN109642579A (zh) 2019-04-16

Similar Documents

Publication Publication Date Title
EP3199814B1 (fr) Compresseur à vis et dispositif à cycle de réfrigération
EP3425202B1 (fr) Compresseur à vis et dispositif à cycle de réfrigération
CN109154455B (zh) 制冷循环装置
KR20090052793A (ko) 냉동 장치 및 압축기
JP4183021B1 (ja) 圧縮機および冷凍装置
JP6058133B2 (ja) スクリュー圧縮機及び冷凍サイクル装置
JP2007138919A (ja) ２段スクリュ圧縮機及びそれを用いた２段圧縮冷凍機
EP3505765B1 (fr) Compresseur à vis et dispositif à cycle frigorifique
US6595024B1 (en) Expressor capacity control
EP3225848A1 (fr) Compresseur à vis et dispositif à cycle de réfrigération
JP2012097645A (ja) 圧縮機
US20230184475A1 (en) Refrigeration cycle apparatus
WO2017094057A1 (fr) Compresseur à vis unique et dispositif à cycle de réfrigération
JP5831345B2 (ja) 冷凍装置
JP2015194294A (ja) 冷凍機
EP3569950B1 (fr) Dispositif à cycle de réfrigération
WO2016088207A1 (fr) Circuit de cycle de réfrigération
JP2013064331A (ja) スクリュー圧縮機および冷凍装置
EP4067659B1 (fr) Compresseur à vis
WO2018146805A1 (fr) Dispositif de réfrigération
WO2018003015A1 (fr) Compresseur à vis unique et dispositif à cycle de réfrigération
JP2012097644A (ja) 圧縮機
WO2018008052A1 (fr) Compresseur à vis et dispositif à cycle de réfrigération
JP2012007859A (ja) 冷凍サイクル装置

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: 20190218

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

A4 Supplementary search report drawn up and despatched

Effective date: 20190717

RIC1 Information provided on ipc code assigned before grant

Ipc: F04C 18/52 20060101ALI20190711BHEP

Ipc: F04C 29/00 20060101ALI20190711BHEP

Ipc: F04C 18/16 20060101ALI20190711BHEP

Ipc: F04C 29/04 20060101AFI20190711BHEP

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
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: 20191205

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: AT

Ref legal event code: REF

Ref document number: 1263726

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200515

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602016035443

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20200429

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200730

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200831

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200729

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200829

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1263726

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200429

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200729

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602016035443

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602016035443

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

26N No opposition filed

Effective date: 20210201

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20200823

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200823

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200831

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200831

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20200831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210302

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200831

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200823

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200823

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200429

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20220712

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230823