JP5272031B2 - Scroll compressor - Google Patents

Abstract

A scroll compressor with high efficiency is provided according to the present invention. The scroll compressor compresses a refrigerant by meshing of an orbiting scroll and a fixed scroll, wherein the orbiting scroll includes a back pressure hole which intermittently connects a compression chamber and a back pressure chamber per one orbit of the orbiting scroll, and the back pressure hole communicates with the compression chamber and also with the back pressure chamber and shuts off the communication with the back pressure chamber after the communication with the compression chamber is shut off.

Description

  The present invention relates to a scroll compressor suitable as a refrigerant compressor used in a refrigeration cycle such as refrigeration or air conditioning, or a gas compressor that compresses air or other gas.

  As a background art of this technical field, a fixed scroll in which a spiral wrap is erected on a base plate, a swirl scroll in which a spiral wrap is erected on an end plate and meshed with the fixed scroll to form a compression chamber, A discharge space for discharging the working fluid compressed in the compression chamber, and a back for pressing at least one of both the orbiting scroll and the fixed scroll against the other provided on the back of at least one of the orbiting scroll and the fixed scroll. The pressure chamber is formed on at least one end plate of the fixed scroll and the orbiting scroll, and the compression chamber and the back pressure chamber are communicated to maintain the pressure in the back pressure chamber at a pressure between the suction pressure and the discharge pressure. A scroll compressor having a back pressure hole is known.

  Patent Document 1 states that “a scroll compressor is a fixed scroll, a orbiting scroll that meshes with the fixed scroll to form a compression chamber, a back pressure chamber provided at the back of the end plate of the orbiting scroll, and the orbiting scroll. A back pressure hole formed in the end plate that connects the compression chamber and the back pressure chamber, and a release that is provided in the end plate of the fixed scroll and releases the working fluid in the compression chamber to the discharge space when the pressure in the compression chamber becomes higher than the pressure in the discharge space A section 47 in which the compression chamber communicates with the back pressure chamber through the back pressure hole in accordance with the orbiting motion of the orbiting scroll is a section 44, 45 in which the compression chamber communicates with the discharge space by the release mechanism. It is configured so as not to overlap. ”(See summary).

JP 2010-106780 A

  In the back pressure hole that intermittently communicates between the compression chamber and the back pressure chamber, after the communication between the compression chamber and the back pressure chamber is completed, the back pressure hole accumulates in the back pressure hole when communicating with the compression chamber that is the next low pressure. Conventionally, no consideration has been given to the occurrence of thermal fluid loss due to re-expansion of the gas and oil into the low-pressure compression chamber.

  An object of the present invention is to provide an efficient scroll compressor.

The object of the present invention is as follows.
A fixed scroll with a spiral wrap on the base plate,
An orbiting scroll that stands up a spiral wrap on the end plate and meshes with the fixed scroll to form a compression chamber;
A discharge space in which the working fluid compressed in the compression chamber is discharged;
A back pressure chamber provided on the back surface of at least one of the orbiting scroll and the fixed scroll, for pressing at least one of both the orbiting scroll and the fixed scroll against the other;
A back pressure hole formed in at least one end plate of the fixed scroll and the orbiting scroll and communicating the compression chamber and the back pressure chamber to hold the pressure in the back pressure chamber at a pressure between the suction pressure and the discharge pressure. And
While the orbiting scroll makes one revolution, the compression chamber and the back pressure chamber are intermittently communicated by the back pressure hole,
This is achieved by a scroll compressor characterized in that the communication port on the back pressure chamber side of the back pressure hole is closed later than the communication port on the compression chamber side of the back pressure hole.

The object of the present invention is as follows.
A fixed scroll with a spiral wrap on the base plate,
An orbiting scroll that stands up a spiral wrap on the end plate and meshes with the fixed scroll to form a compression chamber;
A discharge space in which the working fluid compressed in the compression chamber is discharged;
A back pressure chamber provided on the back surface of the orbiting scroll for pressing the orbiting scroll against the fixed scroll;
A back pressure hole formed in the end plate of the orbiting scroll and communicating the compression chamber and the back pressure chamber to hold the pressure of the back pressure chamber at a pressure between the suction pressure and the discharge pressure;
While the orbiting scroll makes one revolution, the compression chamber and the back pressure chamber are intermittently communicated by the back pressure hole,
This is achieved by a scroll compressor characterized in that the communication port on the back pressure chamber side of the back pressure hole is closed later than the communication port on the compression chamber side of the back pressure hole.

The object of the present invention is as follows.
A scroll compressor that compresses refrigerant by meshing a turning scroll and a fixed scroll,
The orbiting scroll has a back pressure hole that intermittently connects the compression chamber and the back pressure chamber while the orbiting scroll makes one revolution.
The back compression hole communicates with the compression chamber and communicates with the back pressure chamber, and after the communication with the compression chamber is blocked, the communication with the back pressure chamber is blocked. Achieved by machine.

  According to the present invention, an efficient scroll compressor can be obtained.

The top view showing the meshing state of the fixed scroll which is one Example of this invention, and a turning scroll. The example of the longitudinal cross-sectional view of a scroll compressor. The example of the principal part expanded sectional view which expands and shows the back pressure hole part in FIG. The top view showing the meshing state of the fixed scroll of a conventional structure, and a turning scroll. The example of the adiabatic compression diagram which represented typically the relationship between the crank angle in a scroll compressor, and a compression chamber pressure. An example of a shiatsu diagram schematically showing a relationship between a crank angle and a compression chamber pressure in a scroll compressor. The figure which represented typically the pressure change in the opening area of the both ends of a back pressure hole, and a back pressure hole. The conceptual diagram of the refrigerating cycle which shows one Example of this invention.

  Hereinafter, examples will be described with reference to the drawings.

  2 and 3 are longitudinal sectional views of the scroll compressor. As shown in the figure, the fixed scroll (fixed scroll member) 7 includes a disk-shaped base plate 7a, a wrap 7b erected in a spiral shape on the base plate 7a, and an outer peripheral side of the base plate 7a. A cylindrical support portion 7d that is positioned and has an end plate surface 7e continuous with the tip surface of the wrap 7b and surrounds the wrap 7b. Since the wrap 7b is regarded as a “tooth”, the tip end surface of the wrap 7b is called a tooth tip, and the surface of the base plate 7a on which the wrap 7b is erected is between the wraps 7b.

  Further, the surface of the support portion 7 d that contacts the end plate 8 a of the orbiting scroll (orbiting scroll member) 8 is the end plate surface 7 e of the fixed scroll 7. The support portion 7d of the fixed scroll 7 is fixed to the frame 17 by bolts or the like, and the frame 17 integrated with the fixed scroll 7 is fixed to the case (sealed container) 9 by fixing means such as welding.

  The orbiting scroll 8 is disposed so as to face the fixed scroll 7, and the fixed scroll wrap 7 b and the orbiting scroll wrap 8 b are engaged with each other so that the orbiting scroll 8 is disposed in the frame 17. The orbiting scroll 8 has a disc-shaped end plate 8a, a spiral wrap 8b erected from a tooth bottom 8c which is the surface of the end plate 8a, and a boss portion 8d provided at the center of the rear surface of the end plate 8a. Further, the surface of the outer peripheral portion of the end plate 8 a that contacts the fixed scroll 7 is the end plate surface 8 e of the orbiting scroll 8.

  The case 9 has a sealed container structure in which a scroll portion including the fixed scroll 7 and the orbiting scroll 8, a motor portion 16 (16a: rotor, 16b: stator), lubricating oil, and the like are housed. A shaft (rotary shaft) 10 fixed integrally with the rotor 16 a of the motor unit 16 is rotatably supported by the frame 17 via the main bearing 5, and is coaxial with the central axis of the fixed scroll 7.

  A crank portion 10 a is provided at the tip of the shaft 10, and the crank portion 10 a is inserted into a boss portion 8 d provided on the back surface of the orbiting scroll 8. Has been. A swivel bearing 11 is sandwiched between the crank portion 10a and the boss portion 8d. The center axis of the orbiting scroll 8 is decentered by a predetermined distance with respect to the center axis of the fixed scroll 7. The wrap 8b of the orbiting scroll 8 is overlapped with the wrap 7b of the fixed scroll 7 while being shifted by a predetermined angle in the circumferential direction. Reference numeral 12 denotes an Oldham ring for causing the orbiting scroll 8 to relatively rotate with respect to the fixed scroll 7 while restraining it from rotating.

  FIG. 4 is a plan view showing the meshing state of the fixed scroll and the orbiting scroll of the conventional structure. As shown in the figure, a plurality of crescent-shaped compression chambers 13 (13a, 13b) are formed between the wraps 7b, 8b. When the orbiting scroll 8 is orbited, the volume of each compression chamber is continuously reduced as it moves to the center. That is, the orbiting inner line side compression chamber 13a and the orbiting outer line side compression chamber 13b are formed on the inner line side and outer line side of the orbiting scroll wrap 8b, respectively. Reference numeral 20 denotes a suction chamber, which is a space in the middle of sucking fluid. The suction chamber 20 becomes the compression chamber 13 when the phase of the orbiting motion of the orbiting scroll 8 advances and the closing of the fluid is completed.

  The suction port 14 is provided in the fixed scroll 7 as shown in FIGS. The suction port 14 is formed on the outer peripheral side of the base plate 7 a so as to communicate with the suction chamber 20. Further, the discharge port 15 is formed near the spiral center of the base plate 7a of the fixed scroll 7 so as to communicate with the compression chamber 13 on the innermost peripheral side.

  When the shaft 10 is rotationally driven by the motor unit 16, it is transmitted from the crank portion 10 a of the shaft 10 to the orbiting scroll 8 via the orbiting bearing 11, and the orbiting scroll 8 has a turning radius of a predetermined distance around the center axis of the fixed scroll 7. Rotate with. It is restrained by the Oldham ring 12 so that the turning scroll 8 does not rotate during this turning movement.

  By the orbiting motion of the orbiting scroll 8, the compression chamber 13 formed between the laps 7b and 8b is continuously moved to the center, and the volume of the compression chamber 13 is continuously reduced according to the movement. As a result, the fluid sucked from the suction port 14 (for example, refrigerant gas circulating in the refrigeration cycle) is sequentially compressed in each compression chamber 13, and the compressed fluid is discharged from the discharge port 15 to the discharge space 54 above the case. Is done. The discharged fluid enters the motor chamber 52 in the case 9 from the discharge space 54 and is supplied from the discharge pipe 6 to the outside of the compressor, for example, to the refrigeration cycle.

  Lubricating oil is stored at the bottom of the case 9, and a positive displacement or centrifugal oil pump 21 is provided at the lower end of the shaft 10. The oil pump 21 is also rotated with the rotation of the shaft, and the lubricating oil is sucked from the lubricating oil suction port 25 provided in the oil pump case 22 and discharged from the discharge port 28 of the oil pump. The discharged lubricating oil is supplied to the upper portion through a through hole 3 provided in the shaft. A portion of the lubricating oil lubricates the auxiliary bearing 23 through the lateral hole 24 provided in the shaft 10 and returns to the oil reservoir 53 at the bottom of the case. Most of the other lubricating oil passes through the through hole 3 and reaches the upper part of the crank 10a of the shaft 10, and lubricates the slewing bearing 11 through an oil groove 57 provided in the crank 10a. And after lubricating the main bearing 5 provided in the lower part of the slewing bearing 11, it returns to the oil sump 53 of a case bottom part through the oil drain hole 26a and the oil drain pipe 26b.

  Here, a space formed by the oil groove 57 and the orbiting bearing 11 and a space for accommodating the main bearing 5 (frame 17, shaft 10, frame seal 56, collar-shaped orbiting boss provided on the boss portion 8 d of the orbiting scroll 8. The space formed by the member 34 and the seal member 32) is collectively referred to as a first space 33. The first space 33 is a space having a pressure close to the discharge pressure. Most of the lubricating oil flowing into the first space 33 for lubrication of the main bearing 5 and the slewing bearing 11 returns to the bottom of the case through the oil drain hole 26a and the oil drain pipe 26b. The minimum amount necessary for lubrication of the Oldham ring 12 and lubrication and sealing of the sliding portion between the fixed scroll 7 and the orbiting scroll 8 is described later between the upper end surface of the seal member 32 and the end surface of the orbiting boss member 34. The back pressure chamber 18 is entered through the oil leakage means. The back pressure chamber 18 will be referred to as a second space.

  The seal member 32 is inserted into an annular groove 31 provided in the frame 17 together with a wave spring (not shown). Between the first space 33 serving as a discharge pressure and the suction pressure and the discharge pressure. The back pressure chamber 18 which is the pressure is partitioned. The oil leakage means is composed of a plurality of holes 30 provided in the turning boss member 34 and the seal member 32, for example. The plurality of holes 30 perform a circular motion across the seal member 32 in accordance with the orbiting motion of the orbiting scroll 8, and move between the first space 33 and the back pressure chamber 18. Accordingly, the minimum amount of oil can be guided to the back pressure chamber 18 by accumulating the lubricating oil in the first space 33 in the hole 30 and intermittently transferring it to the back pressure chamber 18. Instead of the plurality of holes 30, slits or the like may be provided as oil leakage means to the back pressure chamber.

  When the back pressure increases, the lubricating oil that has entered the back pressure chamber 18 enters the compression chamber 13 through the back pressure hole 35 that connects the back pressure chamber 18 and the compression chamber 13, and is then discharged from the discharge port 15. A part is discharged together with the refrigerant gas from the discharge pipe 6 to the refrigeration cycle, for example, and the rest is separated from the refrigerant gas in the case 9 and stored in the oil sump 53 at the bottom of the case.

  As described above, by providing the first space 33, the back pressure chamber 18, and the oil leakage means, the amount of oil required for each bearing portion and the amount of oil required for the compression chamber can be controlled independently. Therefore, the amount of oil supplied to the compression chamber can be optimized and a highly efficient compressor can be obtained.

  Next, details of the back pressure in the scroll compressor described above will be described. In the scroll compressor, an axial force is generated by the compression action to pull the fixed scroll 7 and the orbiting scroll 8 apart from each other. If the so-called orbiting scroll 8 separation phenomenon occurs in which both scrolls are separated by this axial force, the sealing performance of the compression chamber deteriorates and the efficiency of the compressor decreases. Therefore, a back pressure chamber 18 which is a pressure between the discharge pressure and the suction pressure is provided on the back side of the end plate of the orbiting scroll 8, and the pulling force is canceled by the back pressure and the orbiting scroll 8 is pushed to the fixed scroll 7. I try to put it on. At this time, if the pressing force is too large, sliding loss between the end plate surface 8e of the orbiting scroll 8 and the end plate surface 7e of the fixed scroll 7 increases, and the compressor efficiency decreases. In other words, there is an appropriate value for the back pressure, and if it is too small, the sealing performance of the compression chamber deteriorates and the thermal fluid loss increases, and if it is too large, the sliding loss increases. Therefore, maintaining the back pressure at an appropriate value is important in improving the performance and reliability of the compressor. In the present embodiment, a back pressure hole 35 is provided to maintain the back pressure in an appropriate range.

  The configuration of the back pressure hole 35 will be described in detail with reference to FIGS. The end plate of the orbiting scroll 8 is provided with back pressure holes 35 (35a, 35b, 35c) in a U-shape. The back pressure hole 35 intermittently connects the compression chamber 13 and the back pressure chamber 18 while the orbiting scroll 8 makes one revolution. The stop plug 35d is for closing the end of the passage 35a in order to form a U-shaped back pressure hole 35.

  A notch 36 a communicating with the back pressure chamber 18 is provided on the end plate surface 7 e on the outer peripheral side of the fixed scroll 7. The back pressure chamber side communication port (end portion 35c), which is one communication port of the U-shaped back pressure hole 35, is intermittently communicated with the notch 36a by the turning motion shown in the rotation locus 60 of FIG. The communication port is closed by the end plate surface 7e of the fixed scroll 7 when communicating with the back pressure chamber 18 and not communicating with the notch 36a. The other communication port of the back pressure hole 35, the compression chamber side communication port (end portion 35 b), is intermittently communicated with the compression chamber 13 by the turning motion, and when not communicating, the lap 7 b of the fixed scroll 7 The communication port is blocked.

  The section in which the back pressure chamber side communication port (end portion 35c) communicates with the back pressure chamber 18 and the section in which the compression chamber side communication port (end portion 35b) communicates with the compression chamber are generally different. The compression chamber 13 and the back pressure chamber 18 communicate with each other only during this time.

  When the shape of the notch 36a and the positions of both end portions 35b, 35c of the back pressure hole 35 are determined, a section where the back pressure hole 35 communicates with the compression chamber 13 and the back pressure chamber 18 (a communication section of the back pressure hole). The pressure in the back pressure chamber 18 is a value corresponding to the compression chamber pressure in this communication section. That is, the communication timing is adjusted using the notch 36a.

  This will be described in more detail with reference to FIGS. First, the pressure change in the compression chamber of the scroll compressor will be described with reference to FIG. In the diagram of FIG. 5, the horizontal axis represents the crank angle (phase of the orbiting scroll orbiting), and the vertical axis represents the pressure in the compression chamber during adiabatic compression, and these relationships are schematically shown. The diagram of FIG. 5 shows the compression chamber pressure of one of the swirling outer line side compression chamber 13b and the swirling inner line side compression chamber 13a. Focusing on the compression chamber indicated by the solid line 49 in the figure, the section 70 is a suction section, the section 71 is a compression section, and the section 72 is a discharge section. Reference numerals 73 and 74 show changes in the compression chamber pressure in the compression chambers before and after the compression chamber denoted by 49.

  Next, referring to FIG. 6, the description will be given focusing only on the compression chamber indicated by 49. Reference numeral 49 denotes an adiabatic compression line. The actual acupressure diagram of the adiabatic compression line 49 swells upward like 51 due to thermal fluid loss.

  The conventional configuration will be described as an example. The end portion 35b communicates with the compression chamber 13 in a section 46 from 44 to 45, and the end portion 35c communicates with the back pressure chamber 18 from 48 to 45. It is assumed that it is the section 61. Therefore, the compression chamber 13 and the back pressure chamber 18 communicate with each other in a section 61 that communicates with both ends. In this section 61, the compression chamber pressure fluctuates from 48 to 45, and the back pressure is set to a pressure 47 that is an average of the compression chamber pressure in this section, with some fluctuations.

  The above is the mechanism of back pressure generation. The problems in the conventional configuration will be described below. In the conventional configuration, the back pressure can be properly maintained as described above, but the fact that the U-shaped back pressure hole 35 becomes a so-called dead volume has not been considered much. That is, considering the moment when the back pressure hole 35 ends communication between the compression chamber 13 and the back pressure chamber 18 and the end portion 35b and the end portion 35c are closed together, the back pressure is increased from the end portion 35b side which is the pressure 45. The fluid flows to the end portion 35 c which is (pressure 47), and the back pressure hole 35 is filled with a pressure close to the pressure 45. When the end portion 35 b communicates with the next compression chamber in accordance with the turning motion, the compression chamber pressure is 44. Therefore, the fluid in the back pressure hole 35 is re-expanded from a pressure close to the pressure 45 to the pressure 44. As a result, thermal fluid loss occurs.

  In contrast, in this embodiment, the shape of the notch 36a provided in the fixed scroll 7 is changed as shown in FIG. 1, so that the section 61 in the conventional configuration of FIG. . Specifically, the back pressure hole 35 communicates with the compression chamber 13 and also communicates with the back pressure chamber 18, and after communication with the compression chamber 13 is blocked, communication with the back pressure chamber 18 is blocked. That is, the end portion 35 c communicates with the back pressure chamber 18 even after the end portion 35 b has finished communicating with the compression chamber 13. In other words, while the orbiting scroll 8 makes one revolution, the compression chamber 13 and the back pressure chamber 18 are intermittently communicated by the back pressure hole 35, and the communication port on the back pressure chamber 18 side of the back pressure hole 35 is The end portions 35b and 35c of the back pressure hole 35 are provided so as to have a positional relationship that closes at a later timing than the communication port on the compression chamber 13 side of the back pressure hole 35.

  As a result, the high pressure in the U-shaped back pressure hole 35 after both ends are blocked decreases to the back pressure 47, and the end portion 35b communicates with the next compression chamber with the turning motion. The re-expansion is from the pressure 47 to the pressure 44, and the re-expansion loss can be reduced as compared with the conventional configuration.

  The above contents will be described again with reference to FIG. The upper part of FIG. 7 shows the opening section and the closing section of the end portions 35b and 35c of the back pressure hole, and the lower part of FIG. 7 shows the pressure in the back pressure hole. The solid line shows the structure of this embodiment (FIG. 1), and the broken line shows the opening section and pressure change in the conventional structure (FIG. 4). In the conventional structure (FIG. 4), the pressure becomes 44 at the moment when the end portion 35b opens into the compression chamber (starting point of the section 46), and the pressure in the back pressure hole increases as the compression chamber pressure increases. After the end 35c opens into the back pressure chamber 18 (starting point of the section 61), the pressure rises, and at the end points of the section 46 and the section 61, the pressure 45 'is slightly lower than the pressure 45. Then, when the end portion 35 b opens to the next compression chamber having the pressure 44, the fluid in the back pressure hole re-expands from the pressure 45 ′ to the pressure 44.

  On the other hand, in the structure of this embodiment (FIG. 1), the section 62 is set so that the end 35c is open to the back pressure chamber 18 even after the section 46 is finished. The pressure once increases to 45 'and then decreases to the back pressure 47. When opening the next compression chamber, the fluid in the back pressure hole is re-expanded from the pressure 47 to the pressure 44. However, compared with the conventional structure (FIG. 4), the pressure 45 'to the pressure 47 is increased. The re-expansion amount up to can be reduced.

  The effect of reducing the re-expansion amount increases as the volume of the back pressure hole 35 increases. This is because the re-expansion loss is approximately proportional to V / Vth, where V is the volume of the back pressure hole 35 and Vth is the amount of pressing (suction volume) of the compressor.

  In addition, the effect of reducing the re-expansion amount increases as the pressure in the back pressure hole 35 greatly decreases. Although it is a rough estimate, it is roughly as follows. Assuming that the discharge pressure is Pd, the suction pressure is Ps, and the pressure in the back pressure hole 35 is re-expanded by ΔP (45 ′ → 44 or 47 → 44), the re-expansion loss is approximately proportional to ΔP / (Pd−Ps). .

In other words, the following equation is considered.
Re-expansion loss ∝ (V / Vth) · (ΔP / (Pd−Ps))

  Therefore, the re-expansion loss can be reduced by reducing the pressure in the back pressure hole 35 as 45 '→ 47.

  Further, using the compressor 1 described above, the condenser 40, the expansion valve 41, the evaporator 42, and the four-way valve 43, a refrigeration cycle for air conditioning as shown in FIG. An easy-to-use air conditioner with low power consumption and a wide operating range can be provided.

3 Through-hole 5 Main bearing 6 Discharge pipe 7 Fixed scroll 7a Base plate 7b, 8b Lap 7c, 8c Tooth bottom 7d Support 7e, 8e End plate surface 8 Orbiting scroll 8a End plate 8d Boss portion 9 Case (sealed container)
10 Shaft (Rotating shaft)
DESCRIPTION OF SYMBOLS 10a Crank part 11 Slewing bearing 12 Oldham ring 13 Compression chamber 13a Turning inner line side compression chamber 13b Turning outer line side compression chamber 14 Suction port 15 Discharge port 16 Motor part 16a Rotor 16b Stator 17 Frame 18 Back pressure chamber 20 Suction chamber 21 Oil supply Pump 23 Sub bearing 30 Hole 32 Seal member 33 First space 34 Rotating boss member 35 Back pressure hole 35a Passage 35b Compression chamber side communication port 35c Back pressure chamber side communication port 35d Stopper 36, 36a, 36b Notch 46 Back pressure Section 49 in which hole communication chamber side communication port communicates with compression chamber 49 Adiabatic compression line 51 Finger pressure diagram 52 Motor chamber 53 Oil reservoir 54 Discharge space 60 Rotation locus 61, 62 of back pressure hole communication port Section where pressure chamber side communication port communicates with back pressure chamber

Claims (7)

A fixed scroll with a spiral wrap on the base plate,
An orbiting scroll that stands up a spiral wrap on the end plate and meshes with the fixed scroll to form a compression chamber;
A discharge space in which the working fluid compressed in the compression chamber is discharged;
A back pressure chamber provided on the back surface of at least one of the orbiting scroll and the fixed scroll, for pressing at least one of both the orbiting scroll and the fixed scroll against the other;
A back pressure hole formed in at least one end plate of the fixed scroll and the orbiting scroll and communicating the compression chamber and the back pressure chamber to hold the pressure in the back pressure chamber at a pressure between the suction pressure and the discharge pressure. And
While the orbiting scroll makes one revolution, the compression chamber and the back pressure chamber are intermittently communicated by the back pressure hole,
A scroll compressor, wherein the back pressure chamber side communication port of the back pressure hole is closed later than the back pressure hole side communication port. A fixed scroll with a spiral wrap on the base plate,
An orbiting scroll that stands up a spiral wrap on the end plate and meshes with the fixed scroll to form a compression chamber;
A discharge space in which the working fluid compressed in the compression chamber is discharged;
A back pressure chamber provided on the back surface of the orbiting scroll for pressing the orbiting scroll against the fixed scroll;
A back pressure hole formed in the end plate of the orbiting scroll and communicating the compression chamber and the back pressure chamber to hold the pressure of the back pressure chamber at a pressure between the suction pressure and the discharge pressure;
While the orbiting scroll makes one revolution, the compression chamber and the back pressure chamber are intermittently communicated by the back pressure hole,
A scroll compressor, wherein the back pressure chamber side communication port of the back pressure hole is closed later than the back pressure hole side communication port.   The back pressure chamber side communication port of the back pressure hole is in communication with the back pressure chamber until the communication port on the compression chamber side of the back pressure hole is completely blocked. A featured scroll compressor.   4. The structure according to claim 1, wherein the compression chamber and the back pressure chamber are intermittently communicated by the back pressure hole, and a notch portion that communicates with the back pressure chamber is provided on the end plate of the fixed scroll. A scroll compressor characterized in that a communication port on a back pressure chamber side of the back pressure hole provided in the orbiting scroll is communicated with a part.   A refrigerating cycle device for air conditioning constituted by using the scroll compressor according to any one of claims 1 to 4. A scroll compressor that compresses refrigerant by meshing a turning scroll and a fixed scroll,
The orbiting scroll has a back pressure hole that intermittently connects the compression chamber and the back pressure chamber while the orbiting scroll makes one revolution.
The back compression hole communicates with the compression chamber and communicates with the back pressure chamber, and after the communication with the compression chamber is blocked, the communication with the back pressure chamber is blocked. Machine. In claim 6,
The scroll compressor characterized in that the communication timing is adjusted by using a notch provided in the fixed scroll.

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