JP2009097485A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce the torque variation of a compressor provided with two compression mechanisms of a rotary type and a scroll type. <P>SOLUTION: The compressor 1 includes: a hermetic housing 2; a low stage-side rotary type compression mechanism 3 provided in the housing 2; a high stage-side scroll type compression mechanism 4; and an electric motor 21 for driving both the compression mechanisms 3 and 4. When the rotor 34 of the rotary type compression mechanism is positioned within the range from the position corresponding to the bottom dead center to that after 90° rotation from the bottom dead center, the suction of the scroll type compression mechanism is shut off. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a compressor, and more particularly to a technique for suppressing torque fluctuations in a compressor including a rotary compression mechanism, a scroll compression mechanism, and two compression mechanisms.

  A compressor including a rotary type compression mechanism, a scroll type compression mechanism, and two compression mechanisms has been proposed. For example, in Patent Document 1, an electric motor is provided in one sealed housing, and two compression mechanisms driven by a rotating shaft of the electric motor are provided. One of the two compression mechanisms is a rotary compression mechanism, and the other is Is a scroll-type compression mechanism, one of which is a low-stage side and the other is a high-stage side. In this two-stage compressor, it is described in Patent Document 1 that the low-stage side is preferably constituted by a rotary compression mechanism. According to this two-stage compressor, the low-stage compressor compresses from low pressure to intermediate pressure, and the high-stage compressor compresses from intermediate pressure to high pressure. Compared with the case where the compressor is compressed from low pressure to high pressure, the drawbacks of the individual compressors can be solved, and a small and high performance compressor can be provided.

JP-A-5-87074

The compressor is desired to have a small torque fluctuation in order to suppress the generated vibration. The rotary type compression mechanism has a larger torque fluctuation than the scroll type compression mechanism. According to Patent Document 1, it is described that the torque fluctuation in the rotary compression mechanism can be reduced because the compression ratio is lowered by combining the rotary compression mechanism and the scroll compression mechanism. However, further reduction in torque fluctuation is desired.
The present invention has been made based on such a technical problem, and an object thereof is to reduce torque fluctuations in a compressor including a rotary compression mechanism, a scroll compression mechanism, and two compression mechanisms.

  Under such a purpose, the present inventors examined the behavior of torque fluctuation in the rotary type compression mechanism and the scroll type compression mechanism. The results are shown in FIGS. FIG. 12 is a graph showing the relationship between the rotational angle β (horizontal axis) of the rotor of the rotary compression mechanism and the torque T (vertical axis), and FIG. 13 shows the rotational angle β (horizontal axis) of the orbiting scroll of the scroll compression mechanism. ) And torque T (vertical axis). As shown in FIGS. 12 and 13, it can be seen that the torque fluctuation generated in the rotary compression mechanism is large. In a compressor provided with a rotary type compression mechanism and a scroll type compression mechanism and two compression mechanisms, a torque (total torque) obtained by adding the torque in the rotary type compression mechanism and the torque in the scroll type compression mechanism is generated. Therefore, there is a possibility that a torque fluctuation larger than the torque fluctuation of the rotary type compression mechanism alone will occur in the compressor provided with the two compression mechanisms. On the other hand, as shown in FIG. 13, the scroll compression mechanism has a region where the torque T is relatively large, but also has a region where the torque T is relatively small. Therefore, there is a possibility that the fluctuation of the total torque can be made smaller than the torque fluctuation in the rotary type compression mechanism alone. Therefore, the present inventors have observed changes in the total torque by changing the positional relationship in the rotational direction between the rotary compression mechanism and the scroll compression mechanism in various ways. As a result, when the rotary type compression mechanism and the scroll type compression mechanism are in a specific positional relationship, it has been found that the total torque fluctuation can be made smaller than the torque fluctuation of the rotary type compression mechanism alone.

  Based on the above examination results, the compressor of the present invention drives the hermetic housing, the low-stage compression mechanism and the high-stage compression mechanism provided in the hermetic housing, and the low-stage compression mechanism and the high-stage compression mechanism. An electric motor, wherein one of the low-stage side compression mechanism and the high-stage side compression mechanism is a rotary type compression mechanism and the other is a scroll type compression mechanism, and the rotary type compression mechanism is a rotor And a blade that reciprocates between the top dead center and the bottom dead center as the rotor rotates while the tip is in contact with the rotor, and the rotor corresponds to the position corresponding to the bottom dead center to the bottom dead center. The suction compression of the scroll-type compression mechanism is performed when it is within a range of a position rotated by 90 ° from the position where it is moved.

  In the case of a two-cylinder rotary type compression mechanism, the range of the position where the rotor rotates by −80 ° from the position corresponding to the bottom dead center to the position where the rotor rotates by −100 ° from the position corresponding to the bottom dead center. Or when it is within the range of the position rotated by 80 ° from the position corresponding to the bottom dead center to the position rotated by 100 ° from the position corresponding to the bottom dead center. As a result, the fluctuation of the total torque can be reduced.

The low-stage compression mechanism is a rotary compression mechanism, the high-stage compression mechanism is a scroll compression mechanism, and the scroll compression mechanism further includes a capacity control mechanism including a refrigerant gas discharge port. The suction cutoff is when the discharge port is closed by the orbiting scroll of the scroll type compression mechanism.
Torque fluctuations are particularly problematic when the compressor is operating at low speed, that is, when the compressor is operating using a capacity control mechanism. Therefore, in the case of a compressor provided with a capacity control function, the fact that the discharge port is closed by the orbiting scroll of the scroll type compression mechanism is regarded as the suction cutoff in the present invention.

According to the present invention, the amount of fluctuation of the total torque can be reduced by incorporating the rotary compression mechanism and the scroll compression mechanism into the compressor so as to have a specific positional relationship.

Hereinafter, the present invention will be described in detail based on embodiments shown in the accompanying drawings.
FIG. 1 is a cross-sectional view showing a configuration of a compressor 1 in the present embodiment.
In the compressor 1, a low-stage compression mechanism 3 is installed in the lower part of the sealed housing 2, and a high-stage compression mechanism 4 is installed in the upper part of the sealed housing 2. In addition, an electric motor 21 is installed in the central portion of the hermetic housing 2 and between the low-stage compression mechanism 3 and the high-stage compression mechanism 4. The electric motor 21 includes a stator 22 and a rotor 23. A crankshaft 24 is integrally coupled to the rotor 23. The lower end portion of the crankshaft 24 constitutes a crankshaft 25 for the low-stage side compression mechanism 3, and the upper end portion constitutes a crankshaft 26 of the high-stage side compression mechanism 4. A predetermined amount of lubricating oil 27 is stored at the bottom of the sealed housing 2. The lubricating oil 27 is compressed by the low-stage side compression mechanism 3 and the high-stage side compression through the oil supply hole 11 drilled in the axial direction of the crankshaft 24 by a positive displacement oil pump 28 provided at the lower end of the crankshaft 26. Oil is supplied to a desired lubrication point of the mechanism 4.

The low stage side compression mechanism 3 is constituted by a rotary type compression mechanism. The low-stage compression mechanism 3 has a cylinder chamber 31 and is fixed to the sealed housing 2, an upper bearing 32 and a lower bearing 33 that are respectively installed above and below the cylinder body 30, and a crankshaft 25. And a rotor 34 that is slidably rotated in the cylinder chamber 31, a discharge cover 36 that forms a discharge cavity 35, and a blade 38 (see FIG. 2) that partitions the cylinder chamber 31. A general rotary type compression mechanism can be employed. As shown in FIG. 2, the blade 38 is installed in a slit 39 formed in the cylinder body 30. The slit 39 is formed with a substantially uniform width along the radial direction of the cylinder body 30, and one end opens into the cylinder chamber 31. A spring S is disposed at the other end of the slit 39 and presses the blade 38 toward the rotor 34. The blade 38 reciprocates along the radial direction as the rotor 34 rotates while the tip thereof is in contact with the outer periphery of the rotor 34. A state in which the tip of the blade 38 protrudes most into the cylinder chamber 31 is referred to as a bottom dead center, and a state in which the entire blade 38 enters the slit 39 is referred to as a top dead center.
In the low-stage compression mechanism 3, the refrigerant gas sucked into the cylinder chamber 31 through a suction pipe 37 connected to an accumulator (not shown) is compressed to an intermediate pressure by the rotation of the rotor 34, and then is discharged into the discharge cavity 35. Then, the liquid is discharged and further discharged into the hermetic housing 2 through a discharge port provided in the discharge cover 36.
The intermediate-pressure refrigerant gas discharged into the sealed housing 2 flows into the upper space of the sealed housing 2 through the air gap of the electric motor 21 and is sucked into the high-stage compression mechanism 4.

The high stage side compression mechanism 4 is configured by a scroll type compression mechanism.
The high-stage compression mechanism 4 includes a bearing 40 having a bearing portion 41 that supports the crankshaft 26 from the outer periphery, and a fixed plate 42 that fixes the bearing 40. The fixed plate 42 is fixed to the hermetic housing 2.
The high-stage compression mechanism 4 is formed at the shaft ends of the fixed scroll 43 and the orbiting scroll 44 and the orbiting scroll 44 and the crankshaft 26 that form a pair of compression chambers 45 by engaging with each other while shifting their phases. A drive bushing 46 that is coupled to the crankpin portion 26A to drive the orbiting scroll 44 and an Oldham ring 47 that is provided between the orbiting scroll 44 and the bearing 40 and revolves while preventing the rotation of the orbiting scroll 44. Prepare.
Further, the high-stage compression mechanism 4 is fixed to the discharge valve 48 disposed on the back side of the fixed scroll 43 and the back surface of the fixed scroll 43, and the discharge cover 50 constituting the discharge chamber 49 between the fixed scroll 43. With.

In the high-stage compression mechanism 4, a discharge pipe 51 is connected to the discharge chamber 49, and the refrigerant gas compressed to high temperature and high pressure is discharged out of the compressor 1 in the following manner.
In the high-stage compression mechanism 4, the intermediate-pressure refrigerant gas compressed to the intermediate pressure by the low-stage compression mechanism 3 and discharged into the sealed housing 2 is sucked into the pair of compression chambers 45 through the suction ports 52. The pair of compression chambers 45 are moved to the center side while the volume is reduced by the revolving orbiting of the orbiting scroll 44, and merge to form one compression chamber 45. During this time, the refrigerant gas is compressed from an intermediate pressure to a high pressure (discharge pressure), and is discharged into the discharge chamber 49 through the discharge port 53 formed at the center of the fixed scroll 43. This high-temperature and high-pressure refrigerant gas is discharged to the outside of the compressor 1 through the discharge pipe 51.

The operation of the compressor 1 will be described.
Low-pressure refrigerant gas is sucked into the cylinder chamber 31 from the accumulator (not shown) through the suction pipe 37 into the low-stage compression mechanism 3. The refrigerant gas is compressed to an intermediate pressure by rotating the rotor 34 via the electric motor 21 and the crankshaft 25, and then discharged to the discharge cavity 35. Further, the refrigerant gas is provided from the discharge cavity 35 to the discharge cover 36. It is discharged into the sealed housing 2 through the discharge port. Thereby, the inside of the hermetic housing 2 is set to an intermediate pressure atmosphere, and the electric motor 21 and the lubricating oil 27 are set to a temperature equivalent to the intermediate pressure refrigerant.
The above intermediate pressure refrigerant gas is sucked into the compression chamber 45 of the high-stage compression mechanism 4 through the suction port 52 opened in the sealed housing 2. In the high-stage side compression mechanism 4, the electric motor 21 is driven, and the orbiting scroll 44 is revolved with respect to the fixed scroll 43 through the crankshaft 26, the crankpin portion 26 </ b> A, and the drive bush 46, thereby generating refrigerant. Gas compression is performed. As a result, the intermediate pressure refrigerant gas is compressed to a high pressure state and discharged to the discharge chamber 49 via the discharge valve 48.
The high-temperature and high-pressure refrigerant gas discharged to the discharge chamber 49 is discharged from the compressor 1 through a discharge pipe 51 connected to the discharge chamber 49.

  FIG. 3 is a diagram showing the meshing state of the wrap 43L of the fixed scroll 43 and the wrap 44L of the orbiting scroll 44 at the timing when the compression chamber 45 in which the orbiting scroll 44 and the fixed scroll 43 are closed is formed. Prior to this timing, the compression chamber 45 is open, so the refrigerant gas is sucked. However, after this timing, the tip end portion 43E of the fixed scroll 43 comes into contact with the outer periphery of the orbiting scroll 44, and the tip end portion 44E of the orbiting scroll 44 comes into contact with the outer periphery of the fixed scroll 43. Is done. This state is called suction deadline.

The inventors of the present invention determined the relationship between the deviation angle α and the torque fluctuation amount in the compressor 1 described above. Some results are shown in FIG. Here, the shift angle α is defined as follows. When the blade 38 is in the bottom dead center state in the rotary compression mechanism and in the suction cutoff state in the scroll compression mechanism, the shift angle α between the rotary compression mechanism and the scroll compression mechanism is set to zero. Also, at the position where the rotor 34 rotates 90 ° from the position corresponding to the bottom dead center, if there is no suction cutoff in the scroll compression mechanism, the deviation angle α is 90 °.
4, (a) to (d) are graphs in which the horizontal axis is the rotation angle β of the rotary compression mechanism and the scroll compression mechanism, and the vertical axis is the torque T, where (a) is the deviation angle α. (B) shows the result when the deviation angle α is 180 °, (c) shows the result when the deviation angle α is 180 °, and (d) shows the result when the deviation angle α is 270 °. 4A to 4D, the alternate long and short dash line (Trot) indicates the torque T of the rotary compression mechanism alone, the dotted line (Tscr) indicates the torque T of the scroll compression mechanism alone, and the solid line indicates the rotary compression mechanism. Torque T and the total torque (Ttotal) of the scroll compression mechanism.

  As shown in FIGS. 4A to 4D, the torque T varies depending on the rotation angle β in both the rotary compression mechanism and the scroll compression mechanism, and particularly the torque variation of the rotary compression mechanism is large. Further, as shown in FIGS. 4A to 4D, it can be seen that the variation amount of the total torque differs depending on the deviation angle α. Since this total torque is applied to the crankshaft 24 of the compressor 1, it is desirable that the torque fluctuation indicated by the solid line be small. Therefore, the difference (torque Max−Min) between the maximum value TMax and the minimum value TMin of the total torque indicated by the solid line was determined in the range of the deviation angle α from 0 to 360 ° (−360 °). The result is shown in FIG. Note that the rotation angle β in the rotary compression mechanism is such that the position of the rotor 34 when the blade 38 is at the top dead center is 0 °.

  As shown in FIG. 5, it can be seen that the torque fluctuation amount can be reduced when the deviation angle α is in the range of 0 to 90 °. This is because a portion where the torque T due to the rotary compression mechanism is large and a portion where the torque due to the scroll compression mechanism is small cancel out. From the above results, as shown in FIG. 6, in the present invention, the rotor 34 ranges from a position corresponding to the bottom dead center of the blade 38 to a position rotated by 90 ° from a position corresponding to the bottom dead center of the blade 38. The rotary compression mechanism and the scroll compression mechanism are fixed with respect to the crankshaft 24 (25, 26) so that the suction compression of the scroll compression mechanism is performed. And the torque fluctuation amount of the compressor 1 can be made small by employ | adopting this structure.

  Moreover, the noise which generate | occur | produces from the compressor 1 can be reduced by employ | adopting this structure. That is, the loudest sound is generated in the rotary compression mechanism when the blade 38 reaches the top dead center (rotation angle 0 °). This is because the discharge valve (not shown) of the rotary compression mechanism is closed. Further, a loud noise is generated in the scroll type compression mechanism when the suction is closed. This is because the fixed scroll 43 and the orbiting scroll 44 come into contact with each other. Therefore, when the blade 38 reaches the top dead center in the rotary type compression mechanism, if the suction cutoff is performed in the scroll type compression mechanism, the generated noise becomes remarkable. However, in the compressor 1, when the blade 38 reaches the top dead center in the rotary compression mechanism, the suction cutoff is not performed in the scroll compression mechanism. Therefore, the compressor 1 is also effective in reducing noise.

  Further, the discharge timing of the refrigerant gas of the rotary type compression mechanism is in the range where the rotation angle β is in the range from 180 ° (corresponding to the bottom dead center) to 360 °. Since the compression mechanism can suck the refrigerant gas discharged from the rotary type compression mechanism, it is possible to suppress a decrease in performance due to pressure pulsation.

  By the way, capacity control may be performed in accordance with operating conditions such as a refrigeration apparatus and an air conditioner. For example, in the case of the refrigeration apparatus, the load of the scroll compression mechanism is considerably reduced in the operation state in which the refrigerated state is maintained compared to the operation state in which the refrigeration apparatus is cooled to a desired temperature and frozen. For this reason, capacity control may be performed during low-load operation. Specifically, the discharge amount from the discharge port is controlled by extracting the refrigerant gas being compressed from the compression chamber. The extracted refrigerant gas is again supplied to the suction side of the scroll compression mechanism.

  FIG. 7 is a view showing the vicinity of the scroll type compression mechanism of the compressor 100 provided with the capacity control mechanism. The compressor 100 includes a low-stage compression mechanism 3 including a rotary type compression mechanism, as with the compressor 1. As shown in FIG. 7, a discharge port 60 for capacity control is formed in the fixed scroll 43, and a backflow prevention valve 61 is provided on the back side of the fixed scroll 43 corresponding to the discharge port 60. Yes. In the capacity control, the refrigerant gas in the compression process in the compression chamber 45 is discharged through the discharge port 60, the backflow prevention valve 61, and the capacity control pipe 62. In addition, the code | symbol part same as FIG. 1 is an element similar to the compressor 1 of FIG.

  In the case of the compressor 100 having such a capacity control function, the discharge port 60 is in communication with the compression chamber 45 as shown in FIG. In practice, the intake deadline is not reached. When the turning of the orbiting scroll 44 proceeds, the discharge port 60 is closed by the lap top of the orbiting scroll 44 as shown in FIG. The suction cutoff in the compressor 100 having a capacity control function is the timing when the discharge port 60 is closed. The torque fluctuation is particularly problematic when the compressor 100 is operating at a low speed, that is, when the compressor 100 is operating with capacity control. Therefore, the suction cutoff in the compressor 100 having a capacity control function is set as the timing when the discharge port 60 is closed.

  The compressor 1 shown in FIG. 1 shows an example in which the rotary compression mechanism is a single cylinder (single rotary). However, the present invention can be applied to a compressor 200 having a rotary type compression mechanism having two cylinders (twin rotary) as shown in FIG. 9, and the other parts having the same configuration as the compressor 1 shown in FIG. . The twin rotary includes two cylinder bodies 30a and 30b. The cylinder body 30a has a cylinder chamber 31a, and the cylinder body 30b has a cylinder chamber 31b. A rotor 34a is disposed in the cylinder chamber 31a, and a rotor 34b is disposed in the cylinder chamber 31b. The refrigerant gas sucked into the cylinder chambers 31a and 31b via the suction pipes 37a and 37b connected to the accumulator is compressed by the rotation of the rotors 34a and 34b. The mechanism having the cylinder body 30a as an element is referred to as a first rotary, and the mechanism having the cylinder body 30b as an element is referred to as a second rotary. In addition, the code | symbol part same as FIG. 1 is an element similar to the compressor 1 of FIG.

Although not shown, blades (38) are also provided on the first rotary and the second rotary, respectively. When the blade of the first rotary is at the bottom dead center, the blade is at the top dead center of the second rotary. Further, when the blade of the first rotary is at top dead center, the blade of the second rotary is at bottom dead center. That is, the blade phases of the first rotary and the second rotary are shifted by 180 °.
As described above, the relationship between the deviation angle α and the torque fluctuation was determined for the compressor 200 including the first rotary and the second rotary. The result is shown in FIG. 10, (a) to (d) are graphs in which the horizontal axis is the rotation angle β of the rotary compression mechanism and the scroll compression mechanism, and the vertical axis is the torque T, where (a) is the deviation angle α. (B) shows the result when the deviation angle α is 90 °, (c) shows the result when the deviation angle α is 180 °, and (d) shows the result when the deviation angle α is 270 °. In FIGS. 10A to 10D, the alternate long and short dash line (Trot) indicates the torque T of the rotary compression mechanism (twin rotary) alone, the dotted line (Tscr) indicates the torque T of the scroll compression mechanism alone, and the solid line indicates The sum (Ttotal) of the torque T of the rotary compression mechanism and the torque T of the scroll compression mechanism is shown.

  As shown in FIGS. 10A to 10D, it can be seen that the variation amount of the total torque differs depending on the deviation angle α. Therefore, similarly to the compressor 1, the difference (torque Max−Min) between the maximum value TMax and the minimum value Tmin of the total torque indicated by the solid line is set so that the deviation angle α is in the range of 0 to 360 ° (−360 °). Asked. The result is shown in FIG.

  As shown in FIG. 11, the torque Max-Min is small when the deviation angle α is −80 ° to −100 ° or 80 to 100 °. Therefore, in the case of the twin rotary, the rotor is within the range from the position where the rotor rotates by −80 ° from the position corresponding to the bottom dead center to the position where the rotor rotates by −100 ° from the position corresponding to the bottom dead center. The rotary compression mechanism is configured so that the suction closing of the scroll type compression mechanism is performed when it is within the range of the position rotated by 80 ° from the position corresponding to the dead center to the position rotated by 100 ° from the position corresponding to the bottom dead center. The mold compression mechanism and the scroll compression mechanism are fixed to the crankshaft 24 (25, 26).

  As mentioned above, although embodiment of this invention was described, this invention is not limited to this, A change can be suitably added in the range which does not deviate from the meaning of this invention. For example, a rotary type compression mechanism is applied as the low stage side compression mechanism 3 and a scroll type compression mechanism is applied as the high stage side compression mechanism 4, but this can be reversed.

It is sectional drawing which shows the structure of the compressor to which this invention is applied. It is a top view which shows the structure of a low stage side compression mechanism (rotary type compression mechanism). It is a figure which shows the meshing state of the lap | wrap of a fixed scroll, and the wrap of a turning scroll at the timing which the turning scroll revolved and formed the compression chamber closed with the fixed scroll. 6 is a graph showing a relationship between a blade bottom dead center, a scroll suction cutoff angle α, and a torque fluctuation amount. It is a graph which shows the relationship between deviation angle (alpha) (0-360 degrees (-360 degrees)) and the difference (torque Max-Min) of the maximum value TMax of the total torque, and minimum value TMin. It is a figure which shows typically the relationship between the position of a rotor, and a suction cutoff timing. It is a figure which shows the scroll-type compression mechanism vicinity of the compressor provided with the capacity | capacitance control mechanism. It is a figure which shows the meshing state of the wrap of a fixed scroll and the wrap of a turning scroll in the scroll type compression mechanism of the compressor provided with the capacity | capacitance control mechanism. It is a figure which shows a twin rotary type compression mechanism. 7 is a graph showing the relationship between blade bottom dead center, scroll suction cutoff angle α, and torque fluctuation when a twin rotary compression mechanism is provided. The relationship between the deviation angle α (0 to 360 ° (−360 °)) and the difference between the maximum value TMax and the minimum value Tmin (torque Max−Min) of the total torque when the twin rotary type compression mechanism is provided is shown. It is a graph. It is a graph which shows the relationship between the rotation angle of the rotor of a rotary type compression mechanism, and generated torque. It is a graph which shows the relationship between the rotation angle of the turning scroll of a scroll type compression mechanism, and generated torque.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1,100,200 ... Compressor, 2 ... Sealed housing, 21 ... Electric motor, 3 ... Low stage side compression mechanism (rotary type compression mechanism), 34, 34a, 34b ... Rotor, 38 ... Blade, 4 ... High stage side Compression mechanism (scroll-type compression mechanism), 43 ... fixed scroll, 44 ... orbiting scroll, 60 ... discharge port

Claims (3)

A sealed housing;
A low-stage compression mechanism and a high-stage compression mechanism provided in the sealed housing;
An electric motor that drives the low-stage compression mechanism and the high-stage compression mechanism,
One of the low-stage compression mechanism and the high-stage compression mechanism is a rotary type compression mechanism, and the other is a compressor that is a scroll type compression mechanism,
The rotary compression mechanism includes a rotor, and a blade that reciprocates between a top dead center and a bottom dead center as the rotor rotates while the tip of the rotary compression mechanism is in contact with the rotor.
The rotor is
When it is within the range of the position corresponding to the bottom dead center to the position rotated by 90 ° from the position corresponding to the bottom dead center,
A compressor characterized in that a suction cutoff of the scroll type compression mechanism is performed. A sealed housing;
A low-stage compression mechanism and a high-stage compression mechanism provided in the sealed housing;
An electric motor that drives the low-stage compression mechanism and the high-stage compression mechanism,
One of the low-stage compression mechanism and the high-stage compression mechanism is a two-cylinder rotary type compression mechanism, and the other is a compressor that is a scroll type compression mechanism,
The rotary compression mechanism includes a rotor, and a blade that reciprocates between a top dead center and a bottom dead center as the rotor rotates while the tip of the rotary compression mechanism is in contact with the rotor.
The rotor is
Within a range from a position rotated by −80 ° from a position corresponding to the bottom dead center to a position rotated by −100 ° from a position corresponding to the bottom dead center,
Or
When it is within a range of a position rotated by 80 ° from a position corresponding to the bottom dead center to a position rotated by 100 ° from a position corresponding to the bottom dead center,
A compressor characterized in that a suction cutoff of the scroll type compression mechanism is performed. The low-stage compression mechanism is the rotary compression mechanism, and the high-stage compression mechanism is the scroll compression mechanism,
The scroll compression mechanism includes a capacity control mechanism including a refrigerant gas discharge port;
3. The compressor according to claim 1, wherein when the discharge port is closed by the orbiting scroll of the scroll type compression mechanism, the suction cutoff is defined.

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