WO2018116338A1 - 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
WO2018116338A1
WO2018116338A1 PCT/JP2016/087743 JP2016087743W WO2018116338A1 WO 2018116338 A1 WO2018116338 A1 WO 2018116338A1 JP 2016087743 W JP2016087743 W JP 2016087743W WO 2018116338 A1 WO2018116338 A1 WO 2018116338A1
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WO
WIPO (PCT)
Prior art keywords
gate rotor
rotor support
hole
screw compressor
single screw
Prior art date
Application number
PCT/JP2016/087743
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English (en)
Japanese (ja)
Inventor
栗田　慎
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to CN201690001832.8U priority Critical patent/CN210265126U/zh
Priority to PCT/JP2016/087743 priority patent/WO2018116338A1/fr
Priority to EP16924378.9A priority patent/EP3557064B1/fr
Priority to JP2018557237A priority patent/JP6618638B2/ja
Publication of WO2018116338A1 publication Critical patent/WO2018116338A1/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 refrigeration air conditioner including the same.
  • Single screw compressors are known as one type of positive displacement compressors, and are used, for example, as components of refrigerant circuits built in refrigeration air conditioners.
  • This single screw compressor has a configuration in which a screw having a helical tooth groove and a gate rotor having a plurality of gate rotor teeth that fit into the tooth groove of the screw are housed in a casing forming an outer shell. is there.
  • a tooth space of a screw and a tooth portion of a gate rotor are engaged with each other to form a compression chamber.
  • the single screw compressor In a single screw compressor, when liquid refrigerant is sucked into the compression chamber, liquid compression occurs, and the internal pressure of the compression chamber rises rapidly. When a liquid refrigerant having a higher density than the vaporized refrigerant is sucked into the compression chamber, the internal pressure of the compression chamber increases to a pressure that cannot be reached by gas compression.
  • the single screw compressor is generally configured such that the casing and the screw are made of a metal material such as an iron material and the gate rotor is made of a synthetic resin material to avoid metal contact between the screw and the gate rotor. Therefore, in the single screw compressor, the gate rotor made of a synthetic resin material having a low material strength is destroyed, the compression operation becomes impossible, and the operation stops.
  • Patent Document 1 the internal pressure of the compression chamber is detected using a dedicated detector, and it is determined that liquid compression has occurred when the detected pressure exceeds a preset value, and the discharge is performed.
  • a screw compressor is disclosed in which the position of the slide valve is controlled so as to advance the timing, thereby suppressing an increase in the internal pressure of the compression chamber.
  • the screw compressor of Patent Document 1 is configured to mechanically adjust the position of the slide valve with a dedicated control device when it is determined that liquid compression has occurred because the detected value exceeds the set value.
  • this screw compressor since it takes time to move the slide valve to the target position after liquid compression occurs and the internal pressure of the compression chamber rises, it is possible to start sleep after a long-term stoppage. In the case of rapid liquid compression, it is difficult to suppress an increase in the internal pressure of the compression chamber before the gate rotor is destroyed.
  • the present invention has been made to solve the above-described problems, and suppresses an increase in the internal pressure of a compression chamber due to liquid compression, and prevents a gate rotor from being broken, and a refrigeration equipped with the same.
  • An object is to provide an air conditioner.
  • a single screw compressor includes a casing constituting an outer shell, a screw having a helical tooth groove on an outer peripheral surface, and a plurality of gate rotor teeth that fit into the tooth groove. And a gate rotor that forms a compression chamber, and a plurality of gate rotor support teeth provided facing the plurality of gate rotor teeth, and a gate rotor support that supports the gate rotor.
  • a gate rotor hole is formed in one of the gate rotor teeth so as to penetrate in the tooth thickness direction.
  • One of the gate rotor support teeth is in communication with the gate rotor hole, and the other is in the casing.
  • a gate rotor support hole communicating with the low-pressure space provided is formed through the tooth thickness direction.
  • the gate rotor support hole is provided with a pin that is press-fitted into the gate rotor support hole, and the pin is released from the gate rotor support hole in response to an increase in internal pressure of the compression chamber, and the compression chamber And the low-pressure space are communicated with each other.
  • the single screw compressor according to the present invention and the refrigerating and air-conditioning apparatus including the compressor are configured such that the pin is removed from the gate rotor support hole as the internal pressure of the compression chamber increases, and the compression chamber and the low pressure are passed through the gate rotor hole and the gate rotor support hole. Since the structure communicates with the space, even if the internal pressure of the compression chamber increases due to liquid compression, the increase of the internal pressure of the compression chamber can be suppressed, and the gate rotor can be prevented from being destroyed.
  • FIG. 3 is an enlarged sectional view taken along line AA shown in FIG. 2. It is the top view which showed the gate rotor of the single screw compressor which concerns on Embodiment 1 of this invention.
  • FIG. 5 is a cross-sectional view taken along line BB shown in FIG. 4. It is sectional drawing of the gate rotor and gate rotor support of the single screw compressor which concerns on Embodiment 1 of this invention.
  • Embodiment 1 of the present invention It is a single screw compressor concerning Embodiment 1 of the present invention, and is a sectional view of a gate rotor and a gate rotor support in the state where a pin was press-fitted into a gate rotor support hole. It is sectional drawing of the gate rotor and gate rotor support of the single screw compressor which concerns on Embodiment 2 of this invention. It is sectional drawing of the gate rotor and gate rotor support of the single screw compressor which concerns on Embodiment 3 of this invention. It is the top view which showed the gate rotor of the single screw compressor which concerns on Embodiment 4 of this invention.
  • 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 constituent member of a refrigerant circuit 200 built in the refrigerating and air-conditioning apparatus 100 shown in FIG.
  • the refrigerant circuit 200 includes a single screw compressor 1 that compresses and discharges a refrigerant, a condenser 20 that condenses the refrigerant, a liquid reservoir (not shown) that separates liquid refrigerant and gas refrigerant, and refrigerant.
  • the components such as the expansion valve 21 for reducing the pressure and the evaporator 22 for evaporating the refrigerant are sequentially connected by the refrigerant pipe to form a closed loop.
  • the refrigerating and air-conditioning apparatus 100 includes an inverter (not shown) and a control unit 23 that can communicate with the inverter and receive or transmit a signal.
  • R410 refrigerant, R32 refrigerant, or carbon dioxide refrigerant is used as the refrigerant flowing through the refrigerant circuit 200.
  • FIG. 2 is a cross-sectional view showing the internal structure of the single screw compressor according to Embodiment 1 of the present invention.
  • FIG. 3 is an enlarged cross-sectional view taken along the line AA shown in FIG.
  • FIG. 4 is a plan view showing the gate rotor of the single screw compressor according to Embodiment 1 of the present invention.
  • 5 is a cross-sectional view taken along line BB shown in FIG.
  • FIG. 6 is a cross-sectional view of the gate rotor and the gate rotor support of the single screw compressor according to the first embodiment of the present invention.
  • FIG. 7 is a cross-sectional view of the gate rotor and the gate rotor support in the single screw compressor according to the first embodiment of the present invention in a state where a pin is press-fitted into the gate rotor support hole.
  • the single screw compressor 1 according to the first embodiment a single-stage single screw compressor will be described as an example, but the present invention is not limited to this and may be applied to a two-stage single screw compressor.
  • the single screw compressor 1 according to Embodiment 1 includes a cylindrical casing 2 constituting an outer shell, a compression unit 3 and a drive unit 4 provided inside the casing 2. , Is composed of.
  • a low-pressure space 13 is formed in which low-pressure gas refrigerant flows from the evaporator 22 of the refrigerant circuit 200 and guides the low-pressure gas to the compression unit 3.
  • the compression unit 3 includes a screw 5, a rotating shaft 6, a pair of gate rotors 7 and 7, and gate rotor supports 8 and 8.
  • the screw 5 has a plurality of helical tooth grooves (screw grooves) on the surface of the cylindrical body.
  • the rotary shaft 6 supports the screw 5, and one shaft end portion is rotatably supported by a bearing 50, and the other shaft end portion is connected to the drive unit 4.
  • the gate rotor 7 has a plurality of gate rotor tooth portions 7 a that fit into the tooth grooves of the screw 5, and the screw 5 has a diameter as shown in FIGS. 2 and 3. It is arranged so as to be sandwiched in the direction.
  • the gate rotor support 8 has a plurality of gate rotor support teeth 8a provided to face the plurality of gate rotor teeth 7a, and supports the gate rotor 7.
  • the single screw compressor 1 has a configuration in which two gate rotors 7 and 7 are arranged to face each other by 180 degrees with respect to one screw 5. Therefore, two compression chambers 9 and 9 are formed to face each other by 180 degrees on the upper side of the rotation shaft 6 and the lower side of the rotation shaft 6.
  • the gate rotor 7 has a star shape having eleven gate rotor teeth 7a. Therefore, the gate rotor support 8 is also in the shape of a star having 11 gate rotor support teeth 8 a similar to the gate rotor 7.
  • the gate rotor 7 is made of a synthetic resin material in order to avoid metal contact with the screw 5 made of a metal material. Since the material strength of the gate rotor 7 is lower than that of a metal material, the strength is compensated by being fixed to the upper surface of the gate rotor support tooth portion 8a of the gate rotor support 8 made of a metal material.
  • the gate rotor support 8 is provided so that the gate rotor support tooth portion 8a and the tooth groove of the screw 5 interfere with each other and do not contact the metal. As shown in FIG. 3, both ends of the shaft portion of the gate rotor support 8 are supported by bearings 16 and 17.
  • the single screw compressor 1 includes two variable valves 11, 11 in the compression chambers 9, 9 that vary the internal volume ratio in order to adjust the refrigerant discharge timing.
  • the variable valve 11 has a crescent-shaped rod shape, and is slidably accommodated in a space in which a part of the casing 2 partially protrudes in the radial direction.
  • Each variable valve 11 has a rod 12 fixed to its end face, and is configured to be movable in parallel with the rotary shaft 6 by an axial movement operation of the rod 12.
  • the discharge timing of the refrigerant sucked into the compression chambers 9 and 9 can be adjusted by the variable valve 11 moving in parallel with the rotary shaft 6. That is, the position of the variable valve 11 is controlled by the control unit 23 for the purpose of adjusting the discharge timing so as to increase the energy efficiency.
  • the drive unit 4 is constituted by an electric motor 10.
  • the electric motor 10 includes a stator 10a that is inscribed and fixed in the casing 2 and has a radial gap, and a motor rotor 10b that is rotatably disposed inside the stator 10a.
  • the motor rotor 10 b is connected to the shaft end of the rotary shaft 6 and is disposed on the same axis as the screw 5.
  • the single screw compressor 1 rotates the screw 5 by driving the electric motor 10 to rotate the rotating shaft 6.
  • the electric motor 10 is variably driven by an inverter (not shown), and is operated by accelerating / decelerating the rotational speed of the rotating shaft 6.
  • the single screw compressor 1 electricity is input from the inverter and the electric motor 10 is started.
  • the single screw compressor 1 when the electric motor 10 is activated, the refrigerant is sucked into the pair of compression chambers 9 with substantially the same mass, and the suction of the refrigerant is completed at the same timing.
  • the volume of the compression chamber 9 is reduced and the internal pressure is increased.
  • the single screw compressor 1 when the compression chamber 9 is reduced to the set volume, the compression chamber 9 communicates with the discharge port by the variable valves 11 and 11, and discharge gas is discharged. The timing at which the refrigerant in each compression chamber 9 is discharged is adjusted by controlling the variable valves 11 and 11.
  • the single screw compressor 1 normally only gaseous refrigerant gas is sucked into the compression chamber 9. However, in the single screw compressor 1, the gas-liquid two-phase refrigerant may return from the evaporator 22, and the liquid refrigerant may flow into the single screw compressor 1. In the single screw compressor 1, when the liquid refrigerant is sucked into the compression chamber 9, liquid compression occurs, and the internal pressure of the compression chamber 9 increases rapidly. In the compression chamber 9, since the liquid refrigerant sucked into the chamber has a higher density than the vaporized refrigerant, the internal pressure increases to a pressure that cannot be reached by gas compression. In the single screw compressor 1 having the above configuration, the synthetic resin gate rotor 7 having the lowest material strength among the components of the compression chamber 9 may be damaged, leading to a situation in which the operation cannot be performed.
  • the gate rotor 7 may be broken inside the casing 2, and broken pieces of the gate rotor 7 may be greatly scattered. In that case, the broken piece of the gate rotor 7 may have flowed out to the refrigerant circuit 200 side. In this case, the necessity of cleaning the piping of the refrigerant circuit 200 occurs.
  • the pipe cleaning operation is performed by installing another compressor. It is necessary to disassemble the single screw compressor once in order to remove the broken pieces of the gate rotor scattered in the single screw compressor. The disassembled parts are cleaned and reassembled. The assembled single screw compressor is attached to the cleaned refrigerant circuit and tested. As described above, when the gate rotor 7 is broken, the single screw compressor requires a lot of labor and time for restoration, and also generates a great expense for restoration work.
  • the gate rotor hole 70 has a tooth thickness in one gate rotor tooth portion 7a among the plurality of gate rotor tooth portions 7a. It is formed to penetrate in the direction. As shown in FIG. 6, one of the gate rotor support teeth 8 a of the gate rotor support 8 communicates with the gate rotor hole 70, and the other communicates with the low pressure space 13 provided in the casing 2. A support hole 80 is formed to penetrate in the tooth thickness direction.
  • the gate rotor hole 70 and the gate rotor support hole 80 are formed in a positional relationship such that the cross section is circular and the centers of the circles are on the same axis.
  • the gate rotor hole 70 and the gate rotor support hole 80 are not limited to circular holes, and may be square holes, for example.
  • the gate rotor support hole 80 of the gate rotor support 8 is connected to the first gate rotor support hole 81 communicating with the gate rotor hole 70, one of which is connected to the first gate rotor support hole 81, and the other is low pressure.
  • the second gate rotor support hole 82 communicates with the space 13.
  • the first gate rotor support hole 81 has a smaller diameter than the gate rotor hole 70.
  • the second gate rotor support hole 82 has a larger diameter than the first gate rotor support hole 81.
  • the diameters of the first gate rotor support hole 81 and the second gate rotor support hole 82 are not limited to this.
  • the first gate rotor support hole 81 is provided with a pin 14 that is press-fitted into the first gate rotor support hole 81.
  • the pin 14 is inserted from the gate rotor hole 70 of the gate rotor 7, is disposed so as to straddle between the gate rotor hole 70 and the first gate rotor support hole 81, and is press-fitted in the first gate rotor support hole 81. Is done. Therefore, the outer diameter of the pin 14 is smaller than the inner diameter of the gate rotor hole 70 and larger than the inner diameter of the first gate rotor support hole 81.
  • the pin 14 and the gate rotor support 8 are made of a metal material having substantially the same linear expansion coefficient. If the linear expansion coefficients of the pin 14 and the gate rotor support 8 are different, the pin 14 and the gate rotor support 8 have different expansion rates due to the influence of heat, and the press-fit state of the pin 14 is released regardless of the internal pressure of the compression chamber 9. This is because there is a problem that the pin 14 falls out of the first gate rotor support hole 81.
  • the pin 14 that is press-fitted into the gate rotor support 8 is moved to the first gate rotor support by the target differential pressure.
  • the contact surface pressure of the pin outer peripheral surface, the pin outer diameter, and the contact width with the first gate rotor support hole 81 are set so as to fall vertically downward from the hole 81.
  • the outer diameter of the pin 14 is 2r (mm)
  • the contact width between the outer periphery of the pin 14 and the inner periphery of the first gate rotor support hole 81 shown in FIG. 7 is L (mm)
  • the pin 14 is the first gate rotor support hole 81.
  • the contact surface pressure generated on the outer peripheral surface of the pin 14 by press fitting is defined as P (MPa).
  • the acting force F on the outer peripheral surface of the pin 14 is represented by the following mathematical formula (1).
  • the static friction force F 'of the pin 14 is represented by the following formula (2), where the static friction coefficient is ⁇ .
  • the acting force F ′′ of the pin 14 at the time of liquid compression is expressed by the following formula (3).
  • the pin 14 is the first when the internal pressure of the compression chamber 9 exceeds the target value.
  • deviates from the gate rotor support hole 81 is realizable. That is, in the single screw compressor 1 of the first embodiment, the gate rotor 7 and the gate rotor support 8 are processed so that the above formula (4) is established.
  • the rotational speed detection means 24 for detecting the rotational speed of the single screw compressor 1 and the opening degree of the expansion valve 21 are detected. Opening degree detecting means 25 and notifying means 26 for notifying that the pin 14 is disengaged from the first gate rotor support hole 81.
  • the control unit 23 determines that the rotation speed detection unit 24 has reached the preset maximum rotation speed, the control unit 23 obtains a difference between the opening detected by the opening detection unit 25 at that time and the preset target opening. Then, it is determined whether or not the difference in opening is larger than the target value.
  • the control unit 23 determines that the difference in the opening degree of the expansion valve 21 is larger than the target value the control unit 23 determines that the pin 14 is disengaged from the first gate rotor support hole 81 and notifies the notification unit 26.
  • the control unit 23 incorporates a table of target pulse numbers for the expansion valve 21 when the single screw compressor 1 is operated at the maximum rotational speed based on the condensation temperature and evaporation temperature of the refrigerant circuit 200.
  • the control unit 23 receives the signals of the condensation pulse, the evaporation temperature, and the actual pulse number of the expansion valve 21 at the maximum rotational speed of the single screw compressor 1 in actual operation, and performs a comparison operation with the target pulse number.
  • a control program that determines commands and sends signals is built in.
  • the acting force due to the differential pressure between the compression chamber 9 and the low pressure space 13 is Act on.
  • the pin 14 press-fitted into the first gate rotor support hole 81 of the gate rotor support 8 has a target difference.
  • the contact surface pressure, the pin outer diameter, and the contact width L of the outer peripheral surface of the pin are set so as to fall down vertically by the pressure. Therefore, in the single screw compressor 1, since the refrigerant is sucked evenly into the two compression chambers 9, 9, if liquid compression occurs and the internal pressure of the compression chamber 9 exceeds the target differential pressure, It operates so that the pin 14 falls off.
  • the refrigerant in the compression chamber 9 passes through the gate rotor hole 70 provided in the gate rotor 7 and passes through the gate rotor support hole of the gate rotor support 8. It flows from 80 to the low-pressure space 13. Therefore, in the single screw compressor 1, when liquid compression occurs and the internal pressure of the compression chamber 9 rises, the pin 14 extends from the first gate rotor support hole 81 with a generated stress smaller than the breaking strength of the gate rotor 7.
  • the internal pressure of the compression chamber 9 can be relieved to the low pressure space 13 to prevent the internal pressure of the compression chamber 9 from increasing, and the gate rotor 7 can be destroyed. Can be prevented.
  • the compression chamber 9 and the low pressure space 13 are always communicated with each other via the gate rotor support 8. Therefore, in the single screw compressor 1, since the refrigerant sucked into the compression chamber 9 always leaks to the low pressure side, the refrigerating capacity can be improved in the operation at the same high and low pressure or rotational speed as compared with before the pin 14 is removed. Will fall.
  • the single screw compressor 1 since the compression chamber 9 and the low pressure space 13 communicate with each other when the pin 14 is removed as described above, the refrigerant in the compression chamber 9 leaks into the low pressure space 13.
  • a command signal for increasing the speed is transmitted from the control unit 23 to the inverter so as to compensate for the insufficient refrigeration capacity.
  • the single screw compressor 1 gradually increases in speed, and eventually reaches the maximum rotation speed when the determination that the refrigerating capacity is insufficient is repeated in the control program.
  • the control unit 23 receives the actual number of pulses of the expansion valve 21 at that time and compares it with the target number of pulses.
  • control unit 23 determines that the difference between the actual pulse number and the target pulse number is larger than the target value, the control unit 23 determines that the pin 14 has been removed, and notifies the alarm by the notification means 26.
  • the operator can recognize the necessity of inspection of the single screw compressor 1 by receiving an alarm from the notification means 26.
  • the worker When the worker receives an alarm, the worker temporarily stops the operation of the single screw compressor 1. Next, the operator fully closes the discharge side stop valve 27 and the suction side stop valve 28 of the single screw compressor 1 and bisects the closed loop refrigerant circuit 200. The operator collects only the refrigerant inside the single screw compressor 1 and removes the oil, and then removes the assembly of the gate rotor 7 and the gate rotor support 8 from the inside of the single screw compressor 1 and replaces it with a new one. .
  • the refrigerating and air-conditioning apparatus 100 including the single screw compressor according to the first embodiment is configured to stop the driving of the single screw compressor 1 when the pin 14 is removed from the first gate rotor support hole 81.
  • the structure which prevents the fall of capability may be sufficient. Specifically, when the control unit 23 determines that the rotation speed detection means 24 has reached a preset maximum rotation speed, the difference between the opening degree detected by the opening degree detection means 25 and a preset target opening degree. And determining whether or not the difference in opening is larger than the target value, and determining that the difference in opening is larger than the target value, the pin 14 is disengaged from the first gate rotor support hole 81. Judgment is made and the driving of the single screw compressor 1 is stopped.
  • the pin 14 is removed from the first gate rotor support hole 81 in accordance with the increase in the internal pressure of the compression chamber 9, and the gate rotor hole 70 and the flow path hole 83 are communicated with each other. Even if the internal pressure in the compression chamber 9 becomes a pressure that cannot be reached by normal gas compression due to abrupt liquid compression such as stagnation activation, the gate rotor hole 70 and the gate rotor support hole 80 The compression chamber 9 and the low pressure space 13 can be communicated with each other.
  • the gate rotor hole 70 and the gate rotor support hole 80 function as bypass holes, can prevent the internal pressure of the compression chamber 9 from rising, can prevent the gate rotor 7 from being destroyed, and can perform the compression operation. It can be done well.
  • the single screw compressor 1 of the first embodiment is particularly effective when the R410 refrigerant, the R32 refrigerant, or the carbon dioxide refrigerant that tends to increase the internal pressure in the compression chamber 9 is used as the refrigerant flowing in the refrigerant circuit. can do.
  • the opening degree detection is performed.
  • the pin 14 is disengaged from the first gate rotor support hole 81. Judgment is made and the notification means 26 is notified. Therefore, the operator can recognize the necessity of inspection of the single screw compressor 1 upon receiving an alarm from the notification means 26, and can perform maintenance service to restore the single screw compressor 1.
  • the opening degree detection is performed.
  • the pin 14 is disengaged from the first gate rotor support hole 81. Judgment is made and the driving of the single screw compressor 1 is stopped. Then, the operator can restore the single screw compressor 1 by performing a maintenance service.
  • the single screw compressor 1 of Embodiment 1 can also be implemented by a monogate rotor system in which one gate rotor 7 is provided for one screw 5.
  • the present invention can exhibit the same action and the same effect even in such a single gate rotor type single screw compressor.
  • FIG. 8 is a cross-sectional view of a gate rotor and a gate rotor support of a single screw compressor according to Embodiment 2 of the present invention.
  • symbol is attached
  • the single screw compressor 1 has a flow path hole 83 that allows the low pressure space 13 and the second gate rotor support hole 82 to communicate with each other in addition to the configuration of the first embodiment described above. Is formed on the gate rotor support tooth portion 8a. A plug 15 that closes the second gate rotor support hole 82 is fitted into the second gate rotor support hole 82.
  • the channel hole 83 is formed so as to intersect the second gate rotor support hole 82 from the side surface of the gate rotor support tooth portion 8a. It is desirable that the cross-sectional inner diameter of the flow path hole 83 is slightly smaller than the inner diameter of the first gate rotor support hole 81. This is because the pin 14 that has fallen out of the first gate rotor support hole 81 is received by the flow path hole 83 and retained inside the gate rotor support 8, and the pin 14 can be prevented from jumping out of the gate rotor support 8. The removed pin 14 is then recovered.
  • the plug 15 is provided to hold the pin 14 inside the gate rotor support 8 so that the pin 14 released by the internal pressure of the compression chamber 9 does not come out from the gate rotor support 8 and jump out from below vertically. is there.
  • the plug 15 is fixed inside the second gate rotor support hole 82 by press fitting, shrink fitting, welding, or the like.
  • the plug 15 may have a configuration in which the outer peripheral surface has a screw shape and may be screwed into a screw groove formed on the inner peripheral surface of the second gate rotor support hole 82. Note that the plug 15 does not need to be provided when the pin 14 has another structure that does not come out of the gate rotor support 8, for example, when the pin 14 is held by the channel hole 83 as described above.
  • the pin 14 when the pin 14 is removed from the first gate rotor support hole 81, the refrigerant in the compression chamber 9 passes through the gate rotor hole 70 provided in the gate rotor 7, and the gate rotor support 8 flows from the gate rotor support hole 80 to the low pressure space 13 through the flow path hole 83. Therefore, in the single screw compressor 1, when liquid compression occurs and the internal pressure of the compression chamber 9 rises, the pin 14 extends from the first gate rotor support hole 81 with a generated stress smaller than the breaking strength of the gate rotor 7.
  • the internal pressure of the compression chamber 9 can be relieved to the low pressure space 13 to prevent the internal pressure of the compression chamber 9 from increasing, and the gate rotor 7 can be destroyed. Can be prevented.
  • the pin 14 detached from the first gate rotor support hole 81 is connected to the gate rotor support 8. It can be prevented from jumping out. The pin 14 removed from the first gate rotor support hole 81 can then be recovered.
  • FIG. 9 is a cross-sectional view of a gate rotor and a gate rotor support of a single screw compressor according to Embodiment 3 of the present invention.
  • the single screw compressor which concerns on Embodiment 3 shown in FIG. 9 is based on the structure of the single screw compressor demonstrated in Embodiment 2, it is not limited to this, The single screw of Embodiment 1 It can also be applied to a compressor.
  • symbol is attached
  • the single screw compressor according to the third embodiment includes a first gate rotor hole 71 in which a gate rotor hole 70 is formed on the compression chamber 9 side of the gate rotor 7, and a first gate rotor hole 71.
  • the second gate rotor hole 72 is connected to the first gate rotor hole 71 and the other is connected to the gate rotor support hole 80.
  • the compression chamber 9 side of the gate rotor hole 70 has a dead volume in which fluid is likely to stay, so the energy efficiency is slightly reduced. Therefore, in the single screw compressor of the third embodiment, the gate rotor hole 70 is composed of the first gate rotor hole 71 and the second gate rotor hole 72, and the first gate rotor hole 71 is formed from the second gate rotor hole 72. Since the diameter is small, dead volume can be suppressed.
  • FIG. 10 is a plan view showing a gate rotor of a single screw compressor according to Embodiment 4 of the present invention. Note that the same components as those of the single screw compressor described in the first to third embodiments are denoted by the same reference numerals, and the description thereof is omitted as appropriate.
  • the gate rotor holes 70 are formed through all the gate rotor teeth 7a in the tooth thickness direction, and all the gate rotor support teeth are formed.
  • a gate rotor support hole 80 communicating with the gate rotor hole 70 is formed in the portion 8a so as to penetrate in the tooth thickness direction.
  • the pin 14 is press-fitted into the first gate rotor support hole 81 of each gate rotor support 8.
  • the single screw compressor of the fourth embodiment can increase the flow passage area communicating from the compression chamber 9 to the low pressure space 13 as compared with the single screw compressor of the first to third embodiments. Even when compression occurs and the internal pressure of the compression chamber 9 increases, the increase in the internal pressure of the compression chamber 9 can be further reduced. Therefore, the single screw compressor of Embodiment 4 can prevent the situation where the gate rotor 7 is destroyed more effectively.
  • the present invention has been described above based on the embodiment, the present invention is not limited to the configuration of the embodiment described above.
  • the refrigerant circuit 200 shown in FIG. 1 may have a configuration including other components.
  • the refrigerant flowing through the refrigerant circuit 200 is preferably R410 refrigerant, R32 refrigerant, or carbon dioxide refrigerant, but other refrigerants may be used.
  • the scope of the present invention also includes the scope of various changes, applications, and uses made by those skilled in the art as needed.

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

Abstract

L'invention concerne un compresseur à vis unique pourvu : d'un caisson constituant une coque externe ; d'une vis comprenant une rainure de dent en spirale sur une surface périphérique externe de celle-ci ; un rotor femelle comprenant une pluralité de parties à dent de rotor femelle qui viennent en prise avec la rainure de dent et formant une chambre de compression conjointement avec le caisson et la vis ; et un support de rotor femelle ayant une pluralité de parties à dent de support de rotor femelle qui sont disposées de façon à faire face à la pluralité de parties à dent de rotor femelle et à supporter le rotor femelle. Un trou de rotor femelle est formé dans au moins l'une des parties à dent de rotor femelle de façon à pénétrer à travers celle-ci dans un sens de l'épaisseur des dents. Un trou de support est formé dans une partie à dent de support de rotor femelle de façon à pénétrer à travers celle-ci dans le sens de l'épaisseur des dents, ledit trou de support étant en communication par une extrémité avec le trou de rotor femelle et en communication par l'autre extrémité avec un espace basse pression disposé à l'intérieur du caisson. Une broche emmanchée par pression dans le trou de support est disposée dans le trou de support. La broche se détache lorsque la pression interne de la chambre de compression augmente, réalisant ainsi la communication entre la chambre de compression et l'espace basse pression.
PCT/JP2016/087743 2016-12-19 2016-12-19 Compresseur à vis unique et dispositif de réfrigération/climatisation équipé de celui-ci WO2018116338A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN201690001832.8U CN210265126U (zh) 2016-12-19 2016-12-19 单螺杆压缩机和具备该单螺杆压缩机的制冷空调装置
PCT/JP2016/087743 WO2018116338A1 (fr) 2016-12-19 2016-12-19 Compresseur à vis unique et dispositif de réfrigération/climatisation équipé de celui-ci
EP16924378.9A EP3557064B1 (fr) 2016-12-19 2016-12-19 Compresseur à vis unique et dispositif de réfrigération/climatisation équipé de celui-ci
JP2018557237A JP6618638B2 (ja) 2016-12-19 2016-12-19 シングルスクリュー圧縮機及びそれを備えた冷凍空調装置

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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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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
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

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Publication number Priority date Publication date Assignee Title
FR2624215B1 (fr) * 1987-12-03 1990-05-11 Zimmern Bernard Pignons flottants pour machine a vis haute pression
WO2016199292A1 (fr) * 2015-06-12 2016-12-15 三菱電機株式会社 Compresseur à vis et dispositif de réfrigération

Patent Citations (4)

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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
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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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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EP3557064A4 (fr) 2019-10-23
JPWO2018116338A1 (ja) 2019-03-14
CN210265126U (zh) 2020-04-07
EP3557064A1 (fr) 2019-10-23
JP6618638B2 (ja) 2019-12-11

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