WO2012114455A1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

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Publication number
WO2012114455A1
WO2012114455A1 PCT/JP2011/053841 JP2011053841W WO2012114455A1 WO 2012114455 A1 WO2012114455 A1 WO 2012114455A1 JP 2011053841 W JP2011053841 W JP 2011053841W WO 2012114455 A1 WO2012114455 A1 WO 2012114455A1
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WO
WIPO (PCT)
Prior art keywords
bypass
valve
suction
discharge
passage
Prior art date
Application number
PCT/JP2011/053841
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English (en)
Japanese (ja)
Inventor
遼太 飯島
小山　昌喜
Original Assignee
株式会社日立製作所
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 株式会社日立製作所 filed Critical 株式会社日立製作所
Priority to EP11859605.5A priority Critical patent/EP2679823A1/fr
Priority to JP2013500751A priority patent/JP5489142B2/ja
Priority to PCT/JP2011/053841 priority patent/WO2012114455A1/fr
Publication of WO2012114455A1 publication Critical patent/WO2012114455A1/fr

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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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps

Definitions

  • the present invention relates to a scroll compressor, and is particularly suitable for a scroll compressor that can handle a wide range operation from a high load to a low load.
  • scroll compressors used in air conditioners and water heaters are required to be capable of capacity control over a wide range with a single unit. Yes.
  • the room temperature is generally high at the start of operation, and thus it is necessary to operate rapidly.
  • the inverter control is used to perform high-speed operation (high-speed rotation) with a large capacity at the start, and when the room cools down to some extent and shifts to a steady operation state, the low-speed operation (low-speed rotation) is performed with a small capacity.
  • this low-speed operation in the steady-state operation state has a very low rotational speed, especially assuming that it is used in an air conditioner installed in a building where high heat insulation is deployed, especially in recent energy savings. Driving will be performed.
  • capacity control is performed while maintaining a certain rotational speed. For example, when the room is cooled to some extent, the scroll compressor is stopped and restarted when the room temperature rises. The driving pattern is repeated.
  • Patent Document 1 discloses that a part of the structure of a scroll compressor is improved to perform control to make the discharge amount variable while keeping the rotation speed constant.
  • a bypass passage for bypassing refrigerant gas in the middle of compression to the suction side is provided, and an electromagnetic valve for opening and closing the bypass passage is further provided.
  • the capacity is controlled by discharging the refrigerant gas in the middle to the suction side, and the discharge amount is made variable.
  • the compressed refrigerant can be discharged to the discharge side only after the compression chamber and the bypass passage are first raised from the suction pressure to the discharge pressure.
  • a time delay occurs in discharging the refrigerant to the discharge side, and the refrigerant circulation amount is reduced.
  • the decrease in the refrigerant circulation amount results in a decrease in the work of compression with respect to the power consumption of the compressor, and the compressor efficiency decreases.
  • An object of the present invention is to obtain a scroll compressor capable of improving the discharge delay of the refrigerant to the discharge side when switching from the capacity control operation to the normal operation and realizing high-efficiency capacity control even under low load operation conditions. .
  • the present invention forms a compression chamber by engaging a fixed scroll and a turning scroll provided in an airtight container with each other, and the fixed scroll has a discharge port formed at the center side. And a release port for communicating the compression chamber and the discharge side on the outer peripheral side of the discharge port, and a release valve for preventing a back flow from the discharge side to the compression chamber through the release port,
  • the scroll compressor having a suction chamber and a suction passage communicating with the suction chamber on the outer peripheral side, a bypass passage formed in the fixed scroll and communicating the discharge side with the suction chamber or the suction passage, and the bypass A bypass valve that opens and closes the passage, and is provided on the upstream side of the suction chamber or the portion of the suction passage where the bypass passage opens to prevent backflow to the upstream side Characterized in that it includes a suction check valve.
  • a scroll compressor capable of realizing high-efficiency capacity control even under low load operation conditions. Obtainable.
  • FIG. 1 is a longitudinal sectional view showing a first embodiment of a scroll compressor according to the present invention.
  • FIG. 3 is an enlarged view of a main part of FIG. 2, illustrating a setting range of a bypass passage.
  • FIG. 2 is a cross-sectional view of a main part for explaining the operation during normal operation (bypass valve closing) of the scroll compressor shown in FIG. 1.
  • FIG. 2 is a cross-sectional view of a main part for explaining the operation of the scroll compressor shown in FIG. 1 during bypass operation (bypass valve opening). The diagram explaining the opening / closing control of the bypass valve in Example 1 of this invention.
  • FIG. 10 is a bottom view of the fixed scroll of the scroll compressor shown in FIG. 9 and corresponds to FIG. 2.
  • FIG. 10 is a main part enlarged view showing the structure in the vicinity of the bypass valve in FIG. 9, illustrating the operation during normal operation.
  • FIG. 10 is an enlarged view of a main part showing the structure in the vicinity of the bypass valve in FIG. 9, illustrating a transition state from normal operation to bypass operation.
  • FIG. 10 is a main part enlarged view showing the structure in the vicinity of the bypass valve in FIG. 9, illustrating the operation during bypass operation.
  • FIG. 10 is a main part enlarged view showing the structure in the vicinity of the bypass valve in FIG. 9, illustrating a transition state from the bypass operation to the normal operation.
  • FIG. 1 is a longitudinal sectional view showing Embodiment 1 of the scroll compressor of the present invention.
  • the scroll compressor 1 houses a compression mechanism portion 3 configured by meshing a fixed scroll 5 and a turning scroll 6, an electric motor 4 that drives the compression mechanism portion 3, the compression mechanism portion 3, the electric motor 4, and the like. It is comprised with the airtight container 2 grade
  • the hermetic container 2 includes a cylindrical case 2a constituting the body, a lid chamber 2b welded to the upper portion of the case 2a, and a bottom chamber 2c welded to the lower portion of the case 2a. Yes.
  • a suction pipe 2d is attached to the lid chamber 2b, a discharge pipe 2e is attached to the case 2a, and the inside of the sealed container 2 is a discharge chamber 2f.
  • the compression mechanism section 3 is integrated with a fixed scroll 5 having a spiral wrap 5c standing on a mirror plate 5d, a turning scroll 6 having a spiral wrap 6a standing on a mirror plate 6b, and a bolt 8 integrated with the fixed scroll 5. And a frame 9 that supports the orbiting scroll 6.
  • Reference numeral 7 denotes a crankshaft rotatably supported by a main bearing 9 a provided on the frame 9.
  • An eccentric portion 7 b provided on an upper portion of the crankshaft 7 is a boss portion on the back surface of the orbiting scroll 6. It is connected with the turning scroll 6 through the turning bearing 6c provided in the.
  • An Oldham ring 12 is provided between the lower surface of the orbiting scroll 6 and the frame 9.
  • the Oldham ring 12 includes a groove formed on the lower surface of the orbiting scroll 6 and a groove formed on the frame 9. The revolving (turning) motion is received by receiving the eccentric rotation of the eccentric portion 7b of the crankshaft 7 without rotating the orbiting scroll 6.
  • the electric motor 4 includes a stator 4a and a rotor 4b.
  • the stator 4a is fixed to the hermetic container 2 by means such as press-fitting or welding, and the rotor 4b is fixed to the crankshaft 7 and the fixed It arrange
  • the crankshaft 7 is composed of a main shaft portion 7a and the eccentric portion 7b, and is supported by the main bearing 9a provided on the frame 9 and a sub-bearing 17 attached to the case 2a of the sealed container 2. ing.
  • the eccentric portion 7 b is formed integrally with the main shaft portion 7 a of the crankshaft 7 so as to be eccentric, and is inserted into and engaged with the orbiting bearing 6 c provided on the rear surface of the orbiting scroll 6.
  • the crankshaft 7 is driven by the electric motor 4 to cause the eccentric portion 7b to rotate eccentrically, thereby causing the orbiting scroll 6 to rotate.
  • an oil supply passage 7c for guiding the lubricating oil 13 to the main bearing 9a, the auxiliary bearing 17, the slewing bearing 6c and the like is formed.
  • the refrigerant gas of the refrigeration cycle is introduced into the compression chamber 11 defined by the fixed scroll 5 and the orbiting scroll 6 from the suction pipe 2d when the orbiting scroll 6 is orbited through the crankshaft 7 by the electric motor 4.
  • the compression chamber 11 moves toward the center of the spiral wraps 5c and 6a, the volume is reduced and the compression is performed.
  • the compressed refrigerant gas is discharged to the discharge chamber 2f in the hermetic container 2 from the discharge port 5e provided at the approximate center of the end plate 5d of the fixed scroll 5, and from the discharge pipe 2e to the outside (condenser side of the refrigeration cycle). It flows out.
  • FIGS. 2 is a bottom view of the fixed scroll 5 shown in FIG. 1, which also includes a lap 6a of the orbiting scroll 6,
  • FIG. 3 is an enlarged view of the vicinity of the suction chamber of FIG. 2, and
  • FIG. It is principal part sectional drawing which expands and shows the compressor mechanism part 3 vicinity of the scroll compressor shown.
  • the fixed scroll 5 is provided with a release port 5b for communicating the compression chamber 11 and the discharge chamber 2f on the discharge side, a suction chamber 10 and the discharge chamber 2f.
  • a bypass passage 5f for communication is formed, and the release port 5b is provided with a release valve 5a that is a check valve for preventing a back flow from the discharge side to the compression chamber 11 side.
  • a bypass valve 14 for opening and closing the bypass passage 5f is provided.
  • a suction passage 5h is provided on the upstream side of the suction chamber 10 with which the bypass passage 5f communicates, and a suction check valve 15 is provided on the upstream side (evaporator side) of the suction passage 5h.
  • the suction check valve 15 needs to be provided on the upstream side of the suction chamber 10 or the suction passage 5h where the bypass passage 5f is open, and prevents backflow to the upstream side (evaporator side).
  • FIG. 3 showing an enlarged view of the vicinity of the suction chamber of the fixed scroll 5 shows the wrap position 6a1 of the wrap 6a of the orbiting scroll 6 at the moment when the outer line side compression chamber 21 completes the suction, and the inner line side compression chamber 22 also sucks.
  • the lap position 6a2 at the moment of completing is virtually overlapped.
  • the opening on the suction chamber side of the bypass passage 5f is formed in a suction space shown by a grid in FIG. 3, that is, a compression chamber after the outer line side compression chamber 21 and the inner line side compression chamber 22 have completed the suction. It is preferable not to communicate with each other and to communicate with the suction space at all times, or at a position where the compression chamber communicates at least immediately before completing the suction.
  • this dug portion It is desirable to provide an opening of the bypass passage 5f in A.
  • the bypass valve 14 includes a valve body 14b for opening and closing the bypass passage 5f, and a space 14a for operating the valve body 14b provided on the back side of the valve body 14b (opposite to the fixed scroll 5).
  • a spring 14c provided in the space 14a is provided.
  • the space 14a is provided with a communication pipe 23 so as to communicate with the suction pipe 2d (suction side) and the discharge pipe 2e (discharge side). Further, a portion of the communication pipe 23 outside the sealed container 2 is provided. Is provided with a three-way valve 16. By controlling the three-way valve 16, a refrigerant having a suction pressure or a discharge pressure can be selectively switched and introduced into the space 14a on the back surface of the valve body 14b at an arbitrary timing.
  • valve body 14b If the refrigerant having the suction pressure is introduced into the space 14a, the valve body 14b is operated to open the bypass passage 5f by the pressure difference acting on the valve body 14b and the spring 14c, and if the refrigerant having the discharge pressure is introduced, The valve body 14b is configured to close the bypass passage 5f.
  • connection destination of the communication pipe 23 is switched by the three-way valve 16.
  • the present invention is not limited to this, and the connection destination of the space 14a is switched to the suction side or the discharge side of the compressor.
  • the bypass valve 14 may be opened and closed by introducing a refrigerant having a suction pressure or a discharge pressure into the space 14a.
  • a plurality of electromagnetic valves may be used.
  • FIG. 4 shows a state during normal operation (bypass valve closed) of the scroll compressor 1, that is, the space 14c communicates with the discharge pipe 2e and is filled with the refrigerant having the discharge pressure, and the bypass valve 14 is closed. It is a figure of a state.
  • the arrows in FIG. 4 indicate the flow of the refrigerant.
  • the refrigerant passes through the suction pipe 2d and is sucked from the suction chamber 10 into the compression chamber 11 formed by the meshing of the fixed scroll 5 and the orbiting scroll 6, and the compression chamber 11 is spiral.
  • the refrigerant is compressed and discharged from the discharge port 5e to the discharge chamber 2f.
  • the refrigerant in the discharge chamber 2f is further discharged out of the compressor (outside the sealed container) through the discharge pipe 2e.
  • FIG. 5 shows a state during bypass operation (bypass valve open) of the scroll compressor, that is, a state in which the space 14c communicates with the suction pipe 2d and is filled with the refrigerant having the suction pressure, and the bypass valve 14 is opened.
  • FIG. The arrows in FIG. 5 indicate the flow of the refrigerant.
  • the discharge chamber 2f and the suction chamber 10 communicate with each other through the bypass passage 5f. Since the suction chamber 10 is at the suction pressure when the bypass valve 14 is closed, the refrigerant in the discharge chamber 2f flows into the suction chamber 10 by opening the valve, and the suction chamber 10 becomes the discharge pressure.
  • the suction check valve 15 is provided between the suction chamber 10 and the suction pipe 2d, when the refrigerant in the discharge chamber 2f flows into the suction chamber 10, the suction check valve 15 The valve is closed by the pressure difference between the front and rear, and the suction passage 5h is closed. Therefore, the refrigerant flowing into the suction chamber 10 from the discharge chamber 2f can be prevented from flowing back from the suction chamber 10 toward the suction pipe 2d, and the suction chamber 10 becomes discharge pressure.
  • the release valve 5a is opened just by slightly compressing the refrigerant in the compression chamber 11, and the refrigerant in the compression chamber is discharged from the release port 5b.
  • a flow path that is bypassed to the discharge chamber 2f is formed.
  • the refrigerant discharged into the discharge chamber 2f forms a bypass circulation path that returns to the suction chamber 10 through the bypass passage 5f again. Note that during this bypass operation, the refrigerant is hardly compressed and discharged through the release port 5b to the discharge chamber 2f, so that the power for compressing the refrigerant is small.
  • FIG. 6 is a diagram illustrating opening / closing control of the bypass valve 14 (time change of the bypass valve opening) when capacity control is performed in the scroll compressor of the present embodiment.
  • the bypass valve 14 repeats opening and closing at a constant cycle. Thereby, the above-mentioned normal operation and bypass operation are periodically switched, and the average discharge flow rate of the compressed refrigerant can be reduced while suppressing the compression power to the necessary minimum.
  • the opening / closing control of the bypass valve 14 in the present embodiment is configured such that an arbitrary capacity can be set steplessly between 0 and 100% by making the opening / closing time ratio in one opening / closing cycle variable.
  • an arbitrary capacity can be set steplessly between 0 and 100% by making the opening / closing time ratio in one opening / closing cycle variable.
  • the opening / closing cycle may be constant, but it is preferable to make the length of the cycle variable according to the opening / closing time ratio.
  • the low pressure bypass valve (156) is opened with the high pressure bypass valve (157) closed.
  • the space provided in the upper part of the fixed scroll (bypass mechanism (140) for bypassing the fluid existing in the intermediate region between the suction side and the discharge side) becomes the suction pressure by being connected to the suction side
  • the bypass valve (146) is opened by the differential pressure, and the refrigerant in the compression chamber is discharged from the bypass passage to the suction side while being hardly compressed.
  • the compression chamber is almost filled with the suction pressure during the bypass operation.
  • the present embodiment is greatly different in that the suction chamber 10 and the compression chamber 11 are substantially filled with the discharge pressure during the bypass operation.
  • the scroll compressor that performs the operation of bypassing the refrigerant (bypass operation)
  • FIG. 7 is a diagram for explaining the relationship between the bypass valve opening control, the discharge flow rate of the compressed refrigerant, the compressor input, and the pressure in the conventional example.
  • bypass pressure is the pressure in a space where the pressure changes during bypass operation (hereinafter referred to as bypass space).
  • bypass space the pressure in a space where the pressure changes during bypass operation.
  • the bypass mechanism (140 ) And the pressure of the bypass passage BH.
  • the horizontal axis indicates the passage of time, and the relationship between the discharge flow rate of the compressed refrigerant, the compressor input, and the pressure with respect to the operation of the bypass valve will be described in time series along the passage of time.
  • the compression chamber communicates with the suction side and is filled with the refrigerant having the suction pressure. Moreover, since the said bypass space is also connected with the suction side, it becomes a suction pressure.
  • the low pressure bypass valve When a certain time has passed and the normal operation is resumed, the low pressure bypass valve is closed and compression is started. At this time, the pressure in the bypass space is reduced to the suction pressure. Necessary. For this reason, it takes time to compress and discharge the refrigerant to a pressure higher than the pressure on the discharge side, and there is a time delay between closing the low-pressure bypass valve and discharging the refrigerant. On the other hand, the discharge flow rate is reduced. That is, the conventional one has a problem that causes a reduction in compressor efficiency during capacity control operation.
  • FIG. 8 is a diagram for explaining the relationship between the bypass valve opening degree control, the discharge flow rate of the compressed refrigerant, the compressor input, and the pressure in this embodiment.
  • the bypass space is the suction chamber 10, the compression chamber 11, and the bypass passage 5f
  • the “bypass pressure” in FIG. 8 is the pressure of the suction chamber 10 and the bypass passage 5f.
  • FIG. 8 The diagram of FIG. 8 will be described in time series.
  • the refrigerant is normally compressed and discharged, so that a necessary discharge flow rate is obtained.
  • a normal compressor input is required as power for compressing the refrigerant.
  • the bypass pressure (the pressure in the bypass space) is the suction pressure.
  • the suction chamber 10 communicates with the discharge chamber 2f, the suction chamber 10 and the bypass passage 5f are filled with the discharge pressure, and the compression chamber 11 also becomes the discharge pressure.
  • the present embodiment is characterized in that the bypass pressure becomes substantially the discharge pressure during the bypass operation.
  • the compression chamber 11 When a predetermined time has passed and the bypass valve 14 is closed and returns to normal operation, the compression chamber 11 is already filled with the refrigerant at the discharge pressure, so that there is no need for recompression and the refrigerant is immediately discharged.
  • the normal discharge amount can be secured. That is, according to the present embodiment, it takes no time to compress and discharge the refrigerant to a pressure higher than the discharge side, and the discharge delay can be eliminated. It can prevent that the flow rate decreases and the compressor efficiency decreases. Accordingly, since the discharge amount can be increased as compared with the conventional example, the compressor efficiency during the capacity control operation can be improved.
  • the capacity control according to the present embodiment switches between normal operation and bypass operation at a constant time ratio, the capacity can be varied steplessly in a wide range of 0 to 100% by adjusting the time ratio.
  • the scroll compressor can be used at a rotational speed that can be operated with high efficiency and high reliability.
  • FIGS. 9 to 15 the same reference numerals as those in FIGS. 1 to 8 denote the same or corresponding parts.
  • 9 is a cross-sectional view of the vicinity of the compression mechanism portion of the scroll compressor according to the second embodiment of the present invention
  • FIG. 10 is a bottom view of the fixed scroll of the scroll compressor shown in FIG. It is a figure.
  • bypass valve 14 is controlled to be opened and closed using the pressure of the refrigerant flowing through the suction pipe 2d and the discharge pipe 2e.
  • the second embodiment uses the pressure change in the suction chamber 10.
  • the bypass valve 14 is controlled to open and close.
  • the fixed scroll 5 is provided with a bypass passage 5f that connects the suction chamber 10 and the discharge chamber 2f, and the bypass passage 5f has a discharge chamber side.
  • a bypass valve 14 is provided at the opening.
  • the bypass valve 14 includes a valve body 14b for opening and closing the bypass passage 5f, and a space 14a for operating the valve body 14b provided on the back side of the valve body 14b (the side opposite to the fixed scroll 5).
  • a spring 14c provided in the space 14a is provided.
  • the space 14 a is configured to communicate with the suction chamber 10 through a switch valve passage 5 g formed in the fixed scroll 5.
  • a switch valve 18 for opening and closing the opening is provided at the opening of the switch valve passage 5g on the discharge chamber 2f side.
  • the space 14a becomes the suction chamber.
  • the switch valve 18 is closed, the space 14a is configured so that the communication with the suction chamber 10 is blocked.
  • the switch valve 18 includes a valve body 18a for opening and closing the switch valve passage 5g, a spring 18b for pressing the valve body 18a toward the switch valve passage 5g, and a coil 18c for opening and closing the valve body 18a. ing.
  • the switch valve passage 5g is used only for inflow of refrigerant into the space 14a or outflow from the space 14a of the bypass valve 14 having a small volume, the passage area can be very small, and the valve body 18a. Since the pressure of the refrigerant is small, it is possible to easily open and close the valve body 18a.
  • the bypass passage 5f is provided at the same position as that of the first embodiment shown in FIG. 2, and the switch valve passage 5g is provided in the bypass passage 5f shown in FIG. It is provided in the same range as the connection destination range of the suction chamber side opening.
  • the switch valve passage 5g is connected to a space 14a in the bypass valve 14, and the switch valve can be opened and closed by turning the current to the coil of the switch valve 18 on and off. , Non-communication can be switched arbitrarily. Since other configurations are the same as those of the first embodiment, description thereof is omitted.
  • FIGS. 11 to 14 are enlarged views showing the structure in the vicinity of the bypass valve in FIG. 9.
  • FIG. 11 is a state during normal operation
  • FIG. 12 is a transition state from normal operation to bypass operation
  • FIG. 13 is a state during bypass operation.
  • FIG. 14 is a diagram for explaining a transition state from the bypass operation to the normal operation.
  • the bypass valve 14 and the switch valve 18 are in the state shown in FIG. That is, since the pressure in the compressor is uniform at the time of start-up, the valve body 18a is pushed toward the fixed scroll 5 by the force of the spring 18b and is closed by closing the switch valve passage 5g. Since the pressure in the suction chamber decreases with the operation of the compressor, the bypass valve 14 is kept closed by the pressure difference between the space 14a on the back side and the suction chamber 10 side.
  • FIG. 15 is a diagram for explaining the relationship between the change in the opening degree of the bypass valve 14 with respect to the opening degree control of the switch valve 18, the pressure change in the space 14 a of the bypass valve 14, and the pressure change in the suction chamber 10 in the second embodiment. It is.
  • the scroll compressor capacity control operation can be performed by repeating the above operation. That is, when the switch valve 18 is energized and the switch valve is opened for a short time, the pressure in the space 14a of the bypass valve 14 changes from the discharge pressure to the suction pressure, and thereby the bypass valve 14 is opened, so that the suction chamber 10 becomes the discharge pressure.
  • Bypass operation is performed.
  • the switch valve 18 is energized again and the switch valve is opened for a short time
  • the pressure in the space 14a of the bypass valve 14 changes from the suction pressure to the discharge pressure, whereby the bypass valve 14 is closed and the suction chamber 10 becomes the suction pressure.
  • the duty capacity control operation for controlling the normal operation time and the bypass operation time becomes possible. Therefore, also in the second embodiment, by controlling the ratio (duty ratio) between the normal operation time and the bypass operation time, the discharge amount can be freely controlled and the capacity control operation can be performed.
  • the suction chamber 10 can be kept at the discharge pressure during the bypass operation, the discharge can be started immediately when the bypass valve 14 is closed when switching to the normal operation.
  • the discharge delay to the discharge side of the refrigerant at the time of switching to can be improved.
  • bypass valve 14 and the switch valve 18 necessary for the bypass operation can be provided in the sealed container 2. it can. Therefore, structural parts such as the communication pipe 23 and the three-way valve 16 provided outside the hermetic container 2 as shown in the first embodiment are not necessary, and an effect of being compact and inexpensive can be obtained.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Dans un compresseur à spirale, une chambre de compression (11) est formée par l'emboîtement mutuel d'une spirale fixe (5) et d'une spirale orbitale (6). Une fente d'évacuation (5e) est formée dans la section intermédiaire de la spirale fixe, et dans la périphérie externe de la fente de sortie, la spirale fixe comporte un orifice de décharge (5b) pour faire communiquer la chambre de compression et un côté évacuation, et un clapet de décharge (5a) pour empêcher un reflux de l'orifice de décharge vers la chambre de compression. Une chambre d'admission (10) et un passage d'admission (5h) sont disposés dans la périphérie externe de la spirale fixe. Un passage de dérivation (5f) pour faire communiquer le côté évacuation et la chambre d'admission ou le passage d'admission est formé dans la spirale fixe, et un clapet de dérivation (14) est utilisé pour ouvrir et fermer le passage de dérivation. Plus en amont que la partie de la chambre d'admission ou du passage d'admission où s'ouvre le passage de dérivation, un clapet anti-retour d'admission (15) est prévu pour empêcher un reflux amont. De ce fait, on peut voir une amélioration du retard d'évacuation de fluide frigorigène vers le côté évacuation au cours du passage d'un fonctionnement à commande de capacité à un fonctionnement normal, et une commande de capacité très efficace peut être réalisée même dans des conditions de fonctionnement à faible charge.
PCT/JP2011/053841 2011-02-22 2011-02-22 Compresseur à spirale WO2012114455A1 (fr)

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JP2016169689A (ja) * 2015-03-13 2016-09-23 パナソニックＩｐマネジメント株式会社 スクロール圧縮機
CN105986998A (zh) * 2015-03-19 2016-10-05 艾默生环境优化技术有限公司 可变容积比的压缩机
WO2018092622A1 (fr) * 2016-11-21 2018-05-24 日立ジョンソンコントロールズ空調株式会社 Compresseur à spirale
US9989057B2 (en) 2014-06-03 2018-06-05 Emerson Climate Technologies, Inc. Variable volume ratio scroll compressor
US10066622B2 (en) 2015-10-29 2018-09-04 Emerson Climate Technologies, Inc. Compressor having capacity modulation system
US10094380B2 (en) 2012-11-15 2018-10-09 Emerson Climate Technologies, Inc. Compressor
WO2019138553A1 (fr) * 2018-01-12 2019-07-18 日立ジョンソンコントロールズ空調株式会社 Compresseur à spirale
US10378540B2 (en) 2015-07-01 2019-08-13 Emerson Climate Technologies, Inc. Compressor with thermally-responsive modulation system
US10495086B2 (en) 2012-11-15 2019-12-03 Emerson Climate Technologies, Inc. Compressor valve system and assembly
CN110603381A (zh) * 2017-07-07 2019-12-20 大金工业株式会社 涡旋式压缩机
US10753352B2 (en) 2017-02-07 2020-08-25 Emerson Climate Technologies, Inc. Compressor discharge valve assembly
US10801495B2 (en) 2016-09-08 2020-10-13 Emerson Climate Technologies, Inc. Oil flow through the bearings of a scroll compressor
US10890186B2 (en) 2016-09-08 2021-01-12 Emerson Climate Technologies, Inc. Compressor
US10954940B2 (en) 2009-04-07 2021-03-23 Emerson Climate Technologies, Inc. Compressor having capacity modulation assembly
US10962008B2 (en) 2017-12-15 2021-03-30 Emerson Climate Technologies, Inc. Variable volume ratio compressor
US10995753B2 (en) 2018-05-17 2021-05-04 Emerson Climate Technologies, Inc. Compressor having capacity modulation assembly
US11022119B2 (en) 2017-10-03 2021-06-01 Emerson Climate Technologies, Inc. Variable volume ratio compressor
US11655813B2 (en) 2021-07-29 2023-05-23 Emerson Climate Technologies, Inc. Compressor modulation system with multi-way valve
US11846287B1 (en) 2022-08-11 2023-12-19 Copeland Lp Scroll compressor with center hub
US11965507B1 (en) 2022-12-15 2024-04-23 Copeland Lp Compressor and valve assembly

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US10954940B2 (en) 2009-04-07 2021-03-23 Emerson Climate Technologies, Inc. Compressor having capacity modulation assembly
US11635078B2 (en) 2009-04-07 2023-04-25 Emerson Climate Technologies, Inc. Compressor having capacity modulation assembly
US10907633B2 (en) 2012-11-15 2021-02-02 Emerson Climate Technologies, Inc. Scroll compressor having hub plate
US11434910B2 (en) 2012-11-15 2022-09-06 Emerson Climate Technologies, Inc. Scroll compressor having hub plate
US10094380B2 (en) 2012-11-15 2018-10-09 Emerson Climate Technologies, Inc. Compressor
US10495086B2 (en) 2012-11-15 2019-12-03 Emerson Climate Technologies, Inc. Compressor valve system and assembly
US9989057B2 (en) 2014-06-03 2018-06-05 Emerson Climate Technologies, Inc. Variable volume ratio scroll compressor
JP2016169689A (ja) * 2015-03-13 2016-09-23 パナソニックＩｐマネジメント株式会社 スクロール圧縮機
CN105986998A (zh) * 2015-03-19 2016-10-05 艾默生环境优化技术有限公司 可变容积比的压缩机
US10323638B2 (en) 2015-03-19 2019-06-18 Emerson Climate Technologies, Inc. Variable volume ratio compressor
US10323639B2 (en) 2015-03-19 2019-06-18 Emerson Climate Technologies, Inc. Variable volume ratio compressor
US10378540B2 (en) 2015-07-01 2019-08-13 Emerson Climate Technologies, Inc. Compressor with thermally-responsive modulation system
US10066622B2 (en) 2015-10-29 2018-09-04 Emerson Climate Technologies, Inc. Compressor having capacity modulation system
US10087936B2 (en) 2015-10-29 2018-10-02 Emerson Climate Technologies, Inc. Compressor having capacity modulation system
US10801495B2 (en) 2016-09-08 2020-10-13 Emerson Climate Technologies, Inc. Oil flow through the bearings of a scroll compressor
US10890186B2 (en) 2016-09-08 2021-01-12 Emerson Climate Technologies, Inc. Compressor
CN108884830A (zh) * 2016-11-21 2018-11-23 日立江森自控空调有限公司 涡旋压缩机
US10533555B2 (en) 2016-11-21 2020-01-14 Hitachi-Johnson Controls Air Conditioning, Inc. Scroll compressor
JP2018084157A (ja) * 2016-11-21 2018-05-31 日立ジョンソンコントロールズ空調株式会社 スクロール圧縮機
WO2018092622A1 (fr) * 2016-11-21 2018-05-24 日立ジョンソンコントロールズ空調株式会社 Compresseur à spirale
US10753352B2 (en) 2017-02-07 2020-08-25 Emerson Climate Technologies, Inc. Compressor discharge valve assembly
CN110603381B (zh) * 2017-07-07 2020-06-30 大金工业株式会社 涡旋式压缩机
CN110603381A (zh) * 2017-07-07 2019-12-20 大金工业株式会社 涡旋式压缩机
US11022119B2 (en) 2017-10-03 2021-06-01 Emerson Climate Technologies, Inc. Variable volume ratio compressor
US10962008B2 (en) 2017-12-15 2021-03-30 Emerson Climate Technologies, Inc. Variable volume ratio compressor
WO2019138553A1 (fr) * 2018-01-12 2019-07-18 日立ジョンソンコントロールズ空調株式会社 Compresseur à spirale
US10995753B2 (en) 2018-05-17 2021-05-04 Emerson Climate Technologies, Inc. Compressor having capacity modulation assembly
US11754072B2 (en) 2018-05-17 2023-09-12 Copeland Lp Compressor having capacity modulation assembly
US11655813B2 (en) 2021-07-29 2023-05-23 Emerson Climate Technologies, Inc. Compressor modulation system with multi-way valve
US11879460B2 (en) 2021-07-29 2024-01-23 Copeland Lp Compressor modulation system with multi-way valve
US11846287B1 (en) 2022-08-11 2023-12-19 Copeland Lp Scroll compressor with center hub
US11965507B1 (en) 2022-12-15 2024-04-23 Copeland Lp Compressor and valve assembly

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EP2679823A1 (fr) 2014-01-01
JP5489142B2 (ja) 2014-05-14

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