EP3557064B1 - Compresseur à vis unique et dispositif de réfrigération/climatisation équipé de celui-ci - Google Patents

Compresseur à vis unique et dispositif de réfrigération/climatisation équipé de celui-ci Download PDF

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Publication number
EP3557064B1
EP3557064B1 EP16924378.9A EP16924378A EP3557064B1 EP 3557064 B1 EP3557064 B1 EP 3557064B1 EP 16924378 A EP16924378 A EP 16924378A EP 3557064 B1 EP3557064 B1 EP 3557064B1
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EP
European Patent Office
Prior art keywords
gate
rotor
rotor support
screw compressor
hole
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Active
Application number
EP16924378.9A
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German (de)
English (en)
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EP3557064A4 (fr
EP3557064A1 (fr
Inventor
Shin Kurita
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3557064A4 publication Critical patent/EP3557064A4/fr
Publication of EP3557064A1 publication Critical patent/EP3557064A1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/50—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
    • F04C18/52—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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

Definitions

  • the present invention relates to a single-screw compressor and a refrigerating and air-conditioning apparatus provided with the single-screw compressor.
  • a single-screw compressor is known as a type of displacement compressor, and used, for example, as a component of a refrigerant circuit incorporated in a refrigerating and air-conditioning apparatus.
  • a screw having spiral tooth grooves and a gate rotor having plural gate-rotor teeth which fit in the tooth grooves of the screw are provided in a casing which forms an outer periphery of the compressor.
  • the tooth grooves of the screw and the teeth of the gate rotor are meshed and engaged with each other, forming a compression chamber.
  • the single-screw compressor In the single-screw compressor, when liquid refrigerant is sucked into the compression chamber, liquid compression occurs, thereby suddenly raising the internal pressure of the compression chamber. In the compression chamber, when liquid refrigerant, which is higher in density than vaporized refrigerant, is sucked into the chamber, the internal pressure thereof rises to a level to which it cannot be raised by gas compression.
  • the casing and the screw are made, for example, of metal materials such as iron materials
  • the gate rotor is made of a synthetic resin material, to thereby avoid metal-to-metal contact between the screw and the gate rotor. Therefore, in the single-screw compressor, the gate rotor of the synthetic resin material having a low material strength can be broken, as a result of which the compressor becomes unable to perform its compression operation, and its operation is stopped.
  • the operator recovers refrigerating machine oil from the single-screw compressor, detaches the single-screw compressor from a pipe system of the refrigerant circuit, and carries the single-screw compressor to a workshop where maintenance service can be performed safely and efficiently.
  • the workshop the operator completely disassembles the single-screw compressor and removes fracture fragments of the gate rotor in the casing. After removing the fracture fragments and reassembling the single-screw compressor, the operator resets the single-screw compressor in the refrigerant circuit.
  • the above series of recovery operations require a great deal of time, for which the user is unable to use the refrigerating and air-conditioning apparatus, and further incurs costs as well. This is a big problem for the user.
  • Patent Literature 1 discloses a screw compressor capable of switching between a compressed state and an uncompressed state.
  • Patent Literature 3 deals with a screw machine comprising a sealing portion with limited angular play with respect to the support portion.
  • the screw compressor needs a dedicated detector which detects the internal pressure of the compression chamber, and also needs a pressure sensor capable of outputting an electric signal or a control unit which receives the electric signal, and makes a determination.
  • the manufacturing cost of the screw compressor is higher.
  • the present invention has been made to solve the above problem, and an object of the invention is to provide a single-screw compressor which can reduce raising of the internal pressure of a compression chamber which is caused by liquid compression, and prevent breakage of a gate rotor, and also provide a refrigerating and air-conditioning apparatus provided with the single-screw compressor.
  • a single-screw compressor includes: a casing which forms an outer periphery of the compressor; a screw including spiral tooth grooves formed in its outer peripheral surface; a gate rotor which defines along with the casing and screw a compression chamber, and which includes a plurality of gate-rotor teeth formed to fit in the tooth grooves; and a gate-rotor support which supports the gate rotor, and includes a plurality of gate-rotor support teeth provided to face the plurality of gate-rotor teeth.
  • a gate-rotor hole is formed in at least one of the gate-rotor teeth to extend therethrough in a thickness direction thereof;
  • a gate-rotor support hole is formed in at least one of the gate-rotor support teeth to extend therethrough in a thickness direction thereof, and has ends one of which communicates with the gate-rotor hole and the other of which communicates with a low-pressure space provided in the casing;
  • a pin is provided in the gate-rotor support hole in such a way as to be press-fitted therein; and the pin comes off the gate-rotor support hole when a target pressure difference between the compression chamber and the low-pressure space is achieved.
  • the pin comes off the gate-rotor support hole when the internal pressure of the compression chamber is raised to a level, thereby causing the compression chamber to communicate with the low-pressure space through the gate-rotor hole and gate-rotor support hole. Therefore, even if the internal pressure of the compression chamber is raised by liquid compression, it is possible to reduce the raising of the internal pressure of the compression chamber and thereby prevent breakage of the gate rotor.
  • Fig. 1 is a refrigerant circuit diagram of a refrigerating and air-conditioning apparatus provided with a single-screw compressor according to embodiment 1 of the present invention.
  • the single-screw compressor 1 according to embodiment 1 is used as a component of a refrigerant circuit 200 incorporated in a refrigerating and air-conditioning apparatus 100 as illustrated in Fig. 1 .
  • the refrigerant circuit 200 is configured such that a single-screw compressor 1, a condenser 20, a liquid receiver (not illustrated), an expansion valve 21, an evaporator 22, etc., are sequentially connected by refrigerant pipes, and are provided as a closed loop circuit.
  • the single-screw compressor 1 compresses and discharges refrigerant; the condenser 20 condenses refrigerant; the liquid receiver separates liquid refrigerant and gas refrigerant from each other; the expansion valve 21 decompresses the refrigerant; and the evaporator 22 evaporates the refrigerant.
  • the refrigerating and air-conditioning apparatus 100 includes an inverter not illustrated and a control unit 23 which can communicate with the inverter to receive or send a signal from or to the inverter.
  • the refrigerating and air-conditioning apparatus 100 uses R410 refrigerant, R32 refrigerant, or carbon dioxide refrigerant as refrigerant to be made to flow through the refrigerant circuit 200.
  • Fig. 2 is a sectional view illustrating an internal configuration of the single-screw compressor according to embodiment 1 of the present invention.
  • Fig. 3 is an enlarged sectional view taken along line A-A in Fig. 2 as seen in the direction indicated by arrows A.
  • Fig. 4 is a plan view illustrating a gate rotor of the single-screw compressor according to embodiment 1 of the present invention.
  • Fig. 5 is a sectional view taken along line B-B in Fig. 4 as seen in the directions indicated by arrows B.
  • Fig. 6 is a sectional view of the gate rotor and a gate-rotor support of the single-screw compressor according to embodiment 1 of the present invention.
  • Fig. 7 is a sectional view of the gate rotor and gate-rotor support of the single-screw compressor according to embodiment 1 of the present invention with a pin press-fitted in a gate-rotor support hole.
  • the single-screw compressor 1 according to embodiment 1 will be described by referring to by way of example a single-stage single-screw compressor; however, it is not limited to the single-stage single-screw compressor, and may be applied as a two-stage single-screw compressor.
  • the single-screw compressor 1 according to embodiment 1 includes a cylindrical casing 2 which forms an outer periphery thereof, a compression unit 3 and a drive unit 4 which are provided in the casing 2.
  • a low-pressure space 13 is provided as space into which low-pressure gas refrigerant flows from the evaporator 22 of the refrigerant circuit 200, and in which low-pressure gas is guided to the compression unit 3.
  • the compression unit 3 includes a screw 5, a rotation shaft 6, a pair of gate rotors 7 and gate-rotor supports 8.
  • the screw 5 includes a plurality of spiral tooth grooves (screw grooves) formed in a surface of a cylindrical body.
  • the rotation shaft 6 supports the screw 5, and one of shaft end portions of the rotation shaft 6 is roratably supported by a bearing 50 and the other is coupled to the drive unit 4.
  • the gate rotors 7 each have a plurality of gate-rotor teeth 7a which are formed at an outer periphery thereof to fit in the tooth grooves of the screw 5, and are located to sandwich the screw 5 in a radial direction as illustrated in Figs. 2 and 3 .
  • the gate-rotor supports 8 each include a plurality of gate-rotor support teeth 8a which are located to face the plural gate-rotor teeth 7a, and support the gate rotors 7.
  • the tooth grooves of the screw 5 and the gate-rotor teeth 7a of the gate rotors 7 are meshed and engaged with each other, thereby forming compression chambers 9.
  • two gate rotors 7 are provided on opposite sides with respect to the single screw 5 at positions separated from each other by 180 degrees in a rotation direction.
  • two compression chambers 9 are provided on an upper side and lower side of the rotation shaft 6 at positions separated from each other through 180 degrees in the rotation direction.
  • each of the gate rotors 7 is formed in the shape of a star having eleven gate-rotor teeth 7a. Therefore, each of the gate-rotor supports 8 is also formed in the shape of a star having eleven gate-rotor support teeth 8a, as well as each gate rotor 7.
  • the gate rotor 7 is formed of a synthetic resin material to avoid metal-to-metal contact with the screw 5 formed of a metallic material. The material of the gate rotor 7 is thus lower in material strength than metallic materials. Therefore, in order that the gate rotor 7 be reinforced, the gate rotor 7 is fixed to top surfaces of the gate-rotor support teeth 8a of the gate-rotor support 8 made of a metallic material.
  • the gate-rotor support 8 is provided in such a manner as to avoid metal-to-metal contact between the gate-rotor support teeth 8a and the tooth grooves of the screw 5. It should be noted that as illustrated in Fig. 3 , the gate-rotor support 8 includes a shaft portion both ends of which are supported by bearings 16 and 17.
  • each of the variable valves 11 is rod-shaped to have a section formed in the shape of a crescent, and is slidably provided in space which is shaped by part of the casing 2 that is protruded in the radial direction.
  • Each variable valve 11 has an end face fixed a rod 12, and can be moved parallel to the rotation shaft 6 by moving the rod 12 in an axial direction thereof.
  • the discharge timing of refrigerant sucked into the compression chambers 9 can be adjusted by movement of the variable valves 11 in parallel with the rotation shaft 6. That is, positions of the variable valves 11 are controlled by the control unit 23 for the purpose of adjusting the discharge timing in such a way as to increase an energy efficiency.
  • the drive unit 4 includes an electric motor 10.
  • the electric motor 10 is fixed in such a way as to be inscribed in the casing 2, and includes a stator 10a having space in the radial direction and a motor rotor 10b rotatably provided in the stator 10a.
  • the motor rotor 10b is connected to a shaft end of the rotation shaft 6, and is provided coaxially with the screw 5.
  • the electric motor 10 is driven to rotate the rotation shaft 6, thereby rotating the screw 5. It should be noted that the electric motor 10 is driven at a rotation speed which is variable by an inverter not illustrated, to thereby increase or decrease the rotation speed of the rotation shaft 6.
  • the single-screw compressor 1 When electricity is supplied to the single-screw compressor 1 from the inverter, the electric motor 10 is started.
  • the single-screw compressor 1 when the electric motor 10 is started, refrigerants having substantially the same mass are sucked into the respective compression chambers 9, and the suction of the refrigerants thereinto is completed at the same timing.
  • the volume of each compression chamber 9 is reduced, thus raising the internal pressure thereof.
  • the compression chamber 9 when the volume of each compression chamber 9 is reduced to a set value, the compression chamber 9 is made to communicate with a discharge port by an associated one of the variable valves 11, thus discharging discharge gas. Timings at which the compression chambers 9 are made to discharge the respective refrigerants are adjusted by controlling the respective variable valves 11.
  • the single-screw compressor 1 In the single-screw compressor 1, normally, only refrigerant gas, which is gaseous, is sucked into each compression chamber 9. However, in the single-screw compressor 1, there is a case where two-phase gas-liquid refrigerant returns from the evaporator 22, and liquid refrigerant flows into the single-screw compressor 1. In the single-screw compressor 1, in the case where liquid refrigerant is sucked into the compression chamber 9, liquid compression occurs, thus steeply raising the internal pressure of the compression chamber 9. In the compression chamber 9, the density of the liquid refrigerant sucked therein is higher than that of vaporized refrigerant, and the internal pressure of the chamber is thus raised to a level to which it cannot be raised by gas compression. In the single-screw compressor 1 having the above configuration, the gate rotors 7 made of a synthetic resin which has the lowest material strength among the components of each compression chamber 9 may be broken, and become unable to be operated.
  • the assembled single-screw compressor is installed in the washed refrigerant circuit, and a test run of the single-screw compressor is made.
  • a test run of the single-screw compressor is made.
  • the single-screw compressor in the case where the gate rotor 7 is broken, it takes long time and much trouble to perform the restoration operation, and the restoration operation incurs a considerably high cost.
  • a gate-rotor hole 70 is provided to extend through a gate-rotor tooth 7a of the gate-rotor teeth 7a in a thickness direction thereof.
  • a gate-rotor support hole 80 is provided to extend through a gate-rotor support tooth 8a of the gate-rotor support 8 in a thickness direction of the gate-rotor support tooth 8a, such that one of ends of the gate-rotor support hole 80 communicates with the gate-rotor hole 70, and the other communicates with a low-pressure space 13 provided in the casing 2.
  • the gate-rotor hole 70 and the gate-rotor support hole 80 have circular cross sections, and are located coaxial with each other.
  • the gate-rotor hole 70 and gate-rotor support hole 80 are not limited to circular holes, and may be, for example, square holes.
  • the gate-rotor support hole 80 in the gate-rotor support 8 includes a first gate-rotor support hole 81 which communicates with the gate-rotor hole 70 and a second gate-rotor support hole 82 having ends one of which communicates with the first gate-rotor support hole 81 and the other of which communicates with the low-pressure space 13.
  • the first gate-rotor support hole 81 is smaller in diameter than the gate-rotor hole 70.
  • the second gate-rotor support hole 82 is larger in diameter than the first gate-rotor support hole 81.
  • the diameters of the first gate-rotor support hole 81 and second gate-rotor support hole 82 are not limited to such diameters as described above.
  • a pin 14 is press-fitted in the first gate-rotor support hole 81.
  • the pin 14 is inserted through the gate-rotor hole 70 in the gate rotor 7, located in such a way as to extend between the gate-rotor hole 70 and the first gate-rotor support hole 81, and press-fitted in the first gate-rotor support hole 81. Therefore, the pin 14 is sized such that an outside diameter of the pin 14 is smaller than an inside diameter of the gate-rotor hole 70, and greater than an inside diameter of the first gate-rotor support hole 81.
  • the pin 14 is provided to extend between the gate-rotor hole 70 and first gate-rotor support hole 81, since the gate-rotor hole 70 provided in the gate rotor 7 becomes such a dead volume space.
  • the pin 14 and the gate-rotor support 8 are made of metallic materials having substantially the same coefficient of linear expansion. This is because if the pin 14 and the gate-rotor support 8 have different coefficients of linear expansion, the rates of expansion of the pin 14 and the gate-rotor support 8 are also made to differ from each other under the influence of heat, and a press-fitted state of the pin 14 is lost regardless of the internal pressure of the compression chamber 9, thereby causing the pin 14 to fall off the first gate-rotor support hole 81.
  • a contact pressure on an outer peripheral surface of the pin 14, the outside diameter of the pin 14 and a contact width of the pin 14 which is a width of part of the pin 14 that contacts the first gate-rotor support hole 81 are set such that the pin 14 press-fitted in the gate-rotor support 8 will fall off the first gate-rotor support hole 81 vertically downwards because of a target pressure difference in the case where liquid compression occurs and the internal pressure of the compression chamber 9 thus rises.
  • the pin 14 falls off the first gate-rotor support hole 81 when the internal pressure of the compression chamber 9 becomes higher than or equal to a target value. That is, in the single-screw compressor 1 according to embodiment 1, the gate rotor 7 and gate-rotor support 8 are processed in such a way as to satisfy inequality (4).
  • the refrigerating and air-conditioning apparatus 100 provided with the single-screw compressor 1 according to embodiment 1 as illustrated in Fig. 1 includes a rotation-speed detection unit 24 which detects a rotation speed of the single-screw compressor 1, an opening-degree detection unit 25 which detects an opening degree of the expansion valve 21 and a notification unit 26 which indicates that the pin 14 is located out of the first gate-rotor support holes 81.
  • the control unit 23 determines a difference between an opening degree detected by the opening-degree detection unit 25 at the time when the rotation speed reaches the predetermined maximum rotation speed and a predetermined target opening degree, and determines whether the difference is greater than a target value or not.
  • the control unit 23 determines that the pin 14 is located out of the first gate-rotor support hole 81 and causes the notification unit 26 to make a notification indicating such a fact.
  • control unit 23 incorporates a table of target numbers of pluses of the expansion valve 21 which are determined with respect to the case where the single-screw compressor 1 is operated at a maximum rotation speed, based on condensing temperatures and evaporating temperatures of the refrigerant circuit 200.
  • the control unit 23 incorporates a control program which causes, upon reception of a signal indicating the condensing temperature and evaporating temperature of the refrigerant circuit and the actual number of pulses of the expansion valve 21, which are obtained when the compressor 1 is actually operated at the maximum rotation speed, the control unit 23 to compare the actual number of pulses with a target number of pulses, determine an instruction based on the result of the comparison, and issue a signal.
  • the contact pressure on the outer peripheral surface of the pin, the outside diameter of the pin and the contact width L thereof are set such that the pin 14 press-fitted in the first gate-rotor support hole 81 of each gate-rotor support 8 falls off vertically downwards because of the target pressure difference when the internal pressure of the compression chamber 9 is raised by liquid compression.
  • the refrigerant in the compression chamber 9 passes through the gate-rotor hole 70 provided in the gate rotor 7, and flows into the low-pressure space 13 through the gate-rotor support hole 80 in the gate-rotor support 8.
  • the pin 14 is made to come off the first gate-rotor support hole 81 by a stress smaller than the destruction strength of the gate rotor 7, thus causing the compression chamber 9 to communicate with the low-pressure space 13 and thereby distributing the internal pressure of the compression chamber 9 to the low-pressure space 13, as a result of which the internal pressure of the compression chambers 9 is reduced. Accordingly, it is possible to prevent raising of the internal pressure of the compression chamber 9 and thus prevent breakage of the gate rotor 7.
  • the compression chamber 9 continuously communicates with the low-pressure space 13 through the gate-rotor support 8.
  • the refrigerant sucked into the compression chamber 9 continuously leaks therefrom a low-pressure side, and a refrigeration capacity is reduced lower than before the pin 14 comes off, under the same condition in which the single-screw compressor 1 is operated at the same high/low pressure or at the same rotation speed.
  • the control unit 23 transmits to the inverter a signal instructing the inverter to increase the speed thereof, in order to make up for an insufficient refrigeration capacity.
  • the single-screw compressor 1 gradually increases the rotation speed thereof, and then if it is repeatedly determined in the control program that the refrigeration capacity is insufficient, the rotation speed is eventually increased to the maximum rotation speed.
  • the control unit 23 receives the actual number of pulses of the expansion valve 21 at the time when the rotation speed is set to the maximum rotation speed, and compares the actual number of pulses with the target number of pulses. When determining that the difference between the actual number of pulses and the target number of pulses is greater than a target value, the control unit 23 determines that the pin 14 comes off, and causes the notification unit 26 to issue an alarm. Upon reception of the alarm from the notification unit 26, the operator can recognize that the single-screw compressor 1 needs to be inspected.
  • the operator causes the operation of the single-screw compressor 1 to be stopped once.
  • the operator fully closes a discharge-side stop valve 27 and suction-side stop valve 28 of the single-screw compressor 1, thereby dividing the refrigerant circuit 200, which is provided as the closed loop circuit, into two.
  • the operator recovers only the refrigerant in the single-screw compressor 1, and removes oil from the refrigerant.
  • the operator removes assemblies of the gate rotor 7 and gate-rotor support 8 from the single-screw compressor 1, and replaces the assemblies with new ones.
  • the refrigerating and air-conditioning apparatus 100 provided with the single-screw compressor of embodiment 1 may be configured to stop driving of the single-screw compressor 1 when the pins14 comes off the first gate-rotor support hole 81, and thereby prevent reduction of the refrigeration capacity.
  • the control unit 23 determines the difference between the opening degree detected by the opening-degree detection unit 25 and the predetermined target opening degree, and determines whether the difference is greater than the target value or not.
  • the control unit 23 determines that the pin 14 comes off the first gate-rotor support hole 81, and causes driving of the single-screw compressor 1 to be stopped.
  • the pin 14 comes off the first gate-rotor support hole 81 when the internal pressure of the compression chambers 9 is raised to a level, thereby causing the gate-rotor hole 70 to communicate with a flow-passage hole 83.
  • the compression chamber 9 and the low-pressure space 13 can be made to communicate with each other through the gate-rotor hole 70 and gate-rotor support hole 80.
  • the gate-rotor hole 70 and gate-rotor support hole 80 function as bypass holes, it is possible to prevent raising of the internal pressure of the compression chamber 9, and thus prevent breakage of the gate rotor 7, and cause the compression operation to be satisfactorily performed.
  • the single-screw compressor 1 according to embodiment 1 is more advantageous in the case where R410 refrigerant, R32 refrigerant, or carbon dioxide refrigerant, which tends to cause, especially, the internal pressure of the compression chambers 9 to be raised, are used as refrigerant for use in the refrigerant circuit.
  • the pin 14 and gate-rotor support 8 are made of materials having substantially the same coefficient of linear expansion, it is possible to prevent the press-fitted state of the pin 14 from being lost by the influence of heat, and thus prevent the pin 14 from falling off the first gate-rotor support hole 81.
  • the control unit 23 determines the difference between the opening degree detected by the opening-degree detection unit 25 and the predetermined opening degree. When determining that the difference is greater than the target value, the control unit 23 determines that the pin 14 is located out of the first gate-rotor support hole 81 and causes the notification unit 26 to give an alarm. Thus, upon reception of the alarm from the notification unit 26, the operator can recognize that the single-screw compressor 1 needs to be inspected, and request maintenance services to restore the single-screw compressor 1.
  • the control unit 23 determines the difference between the opening degree detected by the opening-degree detection unit 25 and the predetermined target opening degree. When determining that the difference is greater than the target value, the control unit 23 determines that the pin 14 is located out of the first gate-rotor support holes 81, and stops driving of the single-screw compressor 1. Then, the operator can request maintenance services to restore the single-screw compressor 1.
  • the single-screw compressor 1 according to embodiment 1c can also be put to practical use as a single-gate-rotor type of compressor in which a single gate rotor 7 is provided for a single screw 5, though a detailed illustration of such a type of compressor is omitted.
  • the present invention can achieve the same operations and the same advantages as stated above, even in the case where it is applied to a single-gate-rotor type of single-screw compressor.
  • Fig. 8 is a sectional view of a gate rotor and a gate-rotor support of the single-screw compressor according to embodiment 2 of the present invention. It should be noted that components which are the same as those of the single-screw compressor 1 according to embodiment 1 will be denoted by the same reference signs, and their descriptions will thus be omitted as appropriate.
  • the single-screw compressor 1 has the following configuration: a flow-passage hole 83 which causes the low-pressure space 13 and the second gate-rotor support hole 82 to communicate with each other is formed in the gate-rotor support tooth 8a. Furthermore, a plug 15 is fitted in the second gate-rotor support hole 82 to close it.
  • the flow-passage hole 83 is formed to extend from a side face of the gate-rotor support tooth 8a and intersect the second gate-rotor support hole 82.
  • a cross-sectional inside diameter of the flow-passage hole 83 should be set slightly smaller than the inside diameter of the first gate-rotor support hole 81. This is because if the pin 14 falls off the first gate-rotor support hole 81, it can be caught by the flow-passage hole 83 and held in the gate-rotor support 8 to prevent the pin 14 from jumping out of the gate-rotor support 8. The pin 14 that has come off is recovered later.
  • the plug 15 is provided to hold the pin 14 in the gate-rotor support 8 in order to prevent the pin 14 which has come off because of the internal pressure of the compression chamber 9 from being falling out of the gate-rotor support 8 and jumping out vertically downwards.
  • the plug 15 is fixed to the inside of the second gate-rotor support hole 82 by press fitting, shrink fitting, welding or the like.
  • the plug 15 may be provided with a screwed outer peripheral surface such that it can be screwed into a screw groove formed in an inner peripheral surface of the second gate-rotor support hole 82. It should be noted that the plug 15 does not need to be provided in the case where there is provided another structure for preventing the pin 14 from coming off the gate-rotor support 8, such as a structure for holding the pin 14 using the flow-passage hole 83 as described above.
  • the refrigerant in the compression chamber 9 flows through the gate-rotor hole 70 provided in the gate rotor 7 into the gate-rotor support hole 80 in the gate-rotor support 8, flows into the flow-passage hole 83 from the gate-rotor support hole 80, and then flows into the low-pressure space 13.
  • the pin 14 is made to come off the first gate-rotor support hole 81 by a stress acting thereon that is smaller than a destruction strength of the gate rotor 7, thus causing the compression chamber 9 to communicate with the low-pressure space 13. It is therefore possible to reduce the internal pressure of the compression chambers 9 since it is distributed to the low-pressure space 13, and prevent raising of the internal pressure of the compression chamber 9 and thereby prevent breakage of the gate rotor 7.
  • the pin 14 which has coming off the first gate-rotor support hole 81 can be prevented from jumping out of the gate-rotor support 8.
  • the pin 14 having come off the first gate-rotor support hole 81 can be recovered later.
  • Fig. 9 is a sectional view of a gate rotor and a gate-rotor support of the single-screw compressor according to embodiment 3 of the present invention. It should be noted that although the single-screw compressor according to embodiment 3 as illustrated in Fig. 9 is based on the configuration of the single-screw compressor described in embodiment 2, this is not restrictive, and the single-screw compressor according to embodiment 3 is also applicable to the single-screw compressor 1 according to embodiment 1. It should be noted that components which are the same as those of the single-screw compressors according to embodiments 1 and 2 will be denoted by the same reference numerals, and their descriptions will thus be omitted as appropriate.
  • the gate-rotor hole 70 includes a first gate-rotor hole 71 and a second gate-rotor hole 72.
  • the first gate-rotor hole 71 is formed in part of the gate rotor 7 that is located close to the compression chamber 9; and the second gate-rotor hole 72 has a greater diameter than that of the first rotor hole 71, and one of ends of the second gate-rotor hole 72 communicates with the first gate-rotor hole 71 and the other communicates with the gate-rotor support hole 80.
  • the gate-rotor hole 70 is formed to include the first gate-rotor hole 71 and the second gate-rotor hole 72, and the first gate-rotor hole 71 is made smaller in diameter than the second gate-rotor hole 72, whereby the dead volume can be reduced.
  • Fig. 10 is a plan view illustrating a gate rotor of the single-screw compressor according to embodiment 4 of the present invention. It should be noted that components which are same as those of the single-screw compressors according to embodiments 1 to 3 will be denoted by the same reference numerals, and their descriptions will thus be omitted as appropriate.
  • all the gate-rotor teeth 7a include respective rotor holes 70 which extend therethrough in the thickness direction of the teeth
  • all the gate-rotor support teeth 8a include respective gate-rotor support holes 80 which extend therethough in the thickness direction of the teeth to communication with the gate-rotor holes 70.
  • pins 14 are press-fitted in first gate-rotor support holes 81 of each gate-rotor support 8.
  • the area of the flow passage which extends from the compressor 9 to the low-pressure space 13 can be set greater than those of the single-screw compressors according to embodiments 1 to 3. Therefore, even if liquid compression occurs, and the internal pressure of the compression chambers 9 is raised thereby, the raising of the compression chambers 9 can be further reduced. Thus, the single-screw compressor according to embodiment 4 can further effectively prevent breakage of the gate rotor 7.
  • the present invention is described above by referring to the above embodiments, but the present invention is not limited to the above configurations of the embodiments.
  • the refrigerant circuit 200 as illustrated in Fig. 1 may be formed to include other components.
  • R410 refrigerant, R32 refrigerant, or carbon dioxide refrigerant be used as refrigerant to be made to flow through the refrigerant circuit 200, another refrigerant may be used.

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

Claims (10)

  1. Compresseur à vis unique (1) comprenant :
    un caisson (2) formant une périphérie externe du compresseur à vis unique (1) ;
    une vis (5) incluant une pluralité de rainures de dent en spirale formées dans une surface périphérique externe de la vis (5) ;
    un rotor femelle (7) incluant une pluralité de dents de rotor femelle (7a) formées pour s'emboîter dans les rainures de dent, le rotor femelle (7) définissant avec le caisson (2) et la vis (5) une chambre de compression (9) ; et
    un support de rotor femelle (8) configuré pour supporter le rotor femelle (7), le support de rotor femelle (8) incluant une pluralité de dents de support de rotor femelle (8a) prévues pour faire face à la pluralité de dents de rotor femelle (7a),
    dans lequel un trou de rotor femelle (70) est formé dans au moins une des dents de rotor femelle (7a) de manière à s'étendre à travers l'au moins une des dents de rotor femelle (7a) dans un sens de l'épaisseur de celle-ci, le trou de rotor femelle (70) communiquant avec la chambre de compression (9),
    un trou de support de rotor femelle (80) est formé dans au moins une des dents de support de rotor femelle (8a) de manière à s'étendre à travers l'au moins une des dents de support de rotor femelle (8a) dans un sens de l'épaisseur de celle-ci, le trou de support de rotor femelle (80) ayant des extrémités dont une communique avec le trou de rotor femelle (70), et dont une autre communique avec un espace basse pression (13) prévu dans le caisson (2),
    une broche (14) est emmanchée par pression dans le trou de support de rotor femelle (80), caractérisé en ce que la broche (14) est configurée pour sortir du trou de support de rotor femelle (80) lorsqu'une différence de pression cible est atteinte entre la chambre de compression (9) et l'espace basse pression (13).
  2. Compresseur à vis unique (1) selon la revendication 1, dans lequel :
    le trou de support de rotor femelle (80) inclut :
    un premier trou de support de rotor femelle (81) ayant un diamètre inférieur à celui du trou de rotor femelle (70) et communiquant avec le trou de rotor femelle (70), et
    un second trou de support de rotor femelle (82) ayant un diamètre supérieur à celui du premier trou de support de rotor femelle (81), et ayant des extrémités dont une communique avec le premier trou de support de rotor femelle (81) et dont une autre communique avec l'espace basse pression (13) ; et
    la broche (14) est emmanchée par pression dans le premier trou de support de rotor femelle (81).
  3. Compresseur à vis unique (1) selon la revendication 2, dans lequel un trou de passage d'écoulement (83) est prévu dans au moins une des dents de support de rotor femelle (8a) pour amener l'espace basse pression (13) et le second trou de support de rotor femelle (82) à communiquer l'un avec l'autre à travers le trou de passage d'écoulement (83).
  4. Compresseur à vis unique (1) selon la revendication 3, dans lequel :
    un bouchon (15) est enfoncé dans le second trou de support de rotor femelle (82) pour fermer le second trou de support de rotor femelle (82) ; et
    le trou de passage d'écoulement (83) est conçu pour amener une partie du second trou de support de rotor femelle (82) qui est située entre la broche (14) et le bouchon (15) à communiquer avec l'espace basse pression (13).
  5. Compresseur à vis unique (1) selon l'une quelconque des revendications 1 à 4, dans lequel la broche (14) et le support de rotor femelle (8) sont composés de matériaux métalliques ayant un même coefficient de dilatation linéaire.
  6. Compresseur à vis unique (1) selon l'une quelconque des revendications 1 à 5, dans lequel le trou de rotor femelle (70) inclut :
    un premier trou de rotor femelle (71) composé en partie du rotor femelle (7) qui est situé près de la chambre de compression (9) ; et
    un second trou de rotor femelle (72) ayant un diamètre supérieur à celui du premier trou de rotor femelle (71), et ayant des extrémités dont une communique avec le premier trou de rotor femelle (71) et dont une autre extrémité communique avec le trou de support de rotor femelle (80).
  7. Appareil de réfrigération et de climatisation (100), comprenant :
    un circuit de réfrigération (200) dans lequel le compresseur à vis unique (1) selon l'une quelconque des revendications 1 à 6, un condenseur (20), un détendeur (21) et un évaporateur (22) sont raccordés successivement par des serpentins de réfrigération ; et
    une unité de commande (23) configurée pour commander l'entraînement du compresseur à vis unique (1).
  8. Appareil de réfrigération et de climatisation (100) selon la revendication 7, comprenant en outre :
    une unité de détection de vitesse de rotation (24) configurée pour détecter une vitesse de rotation du compresseur à vis unique (1) ;
    une unité de détection de degré d'ouverture (25) configurée pour détecter un degré d'ouverture du détendeur (21) ; et
    une unité de notification (26) configurée pour présenter une notification indiquant que la broche (14) est située hors du trou de support de rotor femelle (80),
    dans lequel lorsque l'unité de détection de vitesse de rotation (24) détermine que la vitesse de rotation atteint une vitesse de rotation maximale prédéterminée, l'unité de commande (23) est configurée pour déterminer une différence entre le degré d'ouverture détecté par l'unité de détection de degré d'ouverture (25) et un degré d'ouverture cible prédéterminé, et lorsque la détermination que la différence est supérieure à une valeur cible, l'unité de commande (23) est configurée pour déterminer que la broche (14) est située hors du trou de support de rotor femelle (80), et amène l'unité de notification (26) à présenter la notification.
  9. Appareil de réfrigération et de climatisation (100) selon la revendication 7, comprenant en outre :
    une unité de détection de vitesse de rotation (24) configurée pour détecter une vitesse de rotation du compresseur à vis unique (1) ; et
    une unité de détection de degré d'ouverture (25) configurée pour détecter un degré d'ouverture du détendeur (21),
    dans lequel, lorsque l'unité de détection de vitesse de rotation (24) détermine que la vitesse de rotation atteint une vitesse de rotation maximale prédéterminée, l'unité de commande (23) est configurée pour déterminer une différence entre le degré d'ouverture détecté par l'unité de détection de degré d'ouverture (25) et un degré d'ouverture cible prédéterminé, et lorsque la détermination que la différence est supérieure à une valeur cible, l'unité de commande (23) est configurée pour déterminer que la broche (14) est située hors du trou de support de rotor femelle (80), et amène l'interruption de l'entraînement du compresseur à vis unique (1).
  10. Appareil de réfrigération et de climatisation (100) selon l'une quelconque des revendications 7 à 9, dans lequel du frigorigène R410, du frigorigène R32 ou du frigorigène à base de dioxyde de carbone est utilisé en tant que frigorigène destiné à s'écouler dans le circuit de réfrigération (200).
EP16924378.9A 2016-12-19 2016-12-19 Compresseur à vis unique et dispositif de réfrigération/climatisation équipé de celui-ci Active EP3557064B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2016/087743 WO2018116338A1 (fr) 2016-12-19 2016-12-19 Compresseur à vis unique et dispositif de réfrigération/climatisation équipé de celui-ci

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EP3557064A4 EP3557064A4 (fr) 2019-10-23
EP3557064A1 EP3557064A1 (fr) 2019-10-23
EP3557064B1 true EP3557064B1 (fr) 2020-09-23

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EP (1) EP3557064B1 (fr)
JP (1) JP6618638B2 (fr)
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CN110068411A (zh) * 2019-05-14 2019-07-30 天津大学前沿技术研究院 一种测量闸门动水起闭时动摩阻力的试验装置及方法

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Publication number Priority date Publication date Assignee Title
JPS62214293A (ja) * 1986-03-13 1987-09-21 Ebara Corp 回転圧縮機
FR2624215B1 (fr) * 1987-12-03 1990-05-11 Zimmern Bernard Pignons flottants pour machine a vis haute pression
JP2009174520A (ja) * 2007-12-26 2009-08-06 Daikin Ind Ltd ゲートロータおよびスクリュー圧縮機
JP2010255595A (ja) 2009-04-28 2010-11-11 Daikin Ind Ltd スクリュー圧縮機
JP2016017438A (ja) * 2014-07-07 2016-02-01 ダイキン工業株式会社 シングルスクリュー圧縮機
WO2016199292A1 (fr) * 2015-06-12 2016-12-15 三菱電機株式会社 Compresseur à vis et dispositif de réfrigération

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Title
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Also Published As

Publication number Publication date
EP3557064A4 (fr) 2019-10-23
JPWO2018116338A1 (ja) 2019-03-14
WO2018116338A1 (fr) 2018-06-28
CN210265126U (zh) 2020-04-07
EP3557064A1 (fr) 2019-10-23
JP6618638B2 (ja) 2019-12-11

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