JP2017172343A - Rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a high efficiency rotary compressor in which a refrigerant leakage between an inside part of a closed container and an inside part of a compression chamber is reduced.SOLUTION: A rotary compressor C of this invention comprises in a closed vessel 1: an electric motor M; a crank shaft 5 rotationally driven by the electric motor M and having compression members 5A, 5B, 11 and 12 thereon; cylinders 7 and 8 having a compression chamber 9 where refrigerant is compressed through rotational driving of the compression members 5A, 5B, 11 and 12; a main bearing 6 for closing the cylinders 7 and 8 at one part in an axis direction and a sub-bearing 10 for closing at the other in an axis direction. The cylinders 7 and 8, the main bearing 6 and the sub-bearing 10 have component fastening holes 7A, 7B, 8A, and 8B in an axial direction, all holes 8C, 8D and 8E extending in an axial direction other than the component fastening holes 7A, 7B, 8A and 8B are arranged at a longer side in view of time where a pressure difference between the inside of the closed container and the inside of the compression chamber becomes low in a range of crank angle of the crank shaft of 180° or less or 180° or more.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a rotary compressor.

Conventionally, the structure described in Patent Document 1 is already known as a rotary compressor. In addition, the code | symbol in the following parenthesis is a code | symbol used in FIG. 1, FIG. 2, etc. of patent document 1. FIG.
The rotary compressor of Patent Document 1 includes a main bearing (9) in a compression chamber surrounded by a cylinder (2) and a main bearing (9) and end bearings (10) that close both ends of the cylinder (2). And a piston (4) that is eccentrically rotated by a crankshaft (3) that is pivotally supported by the end bearing (10), and is always in contact with the outer peripheral surface of the piston (4) so that the inside of the compression chamber has a high pressure side and a low pressure side. It is a rotary compressor which accommodated in the airtight container (1) the compression element (11) attached to the cylinder (2) with the vane (5) classified into (2), and the electric motor which drives the compression element (11).

  In the rotary compressor, a hole penetrating the cylinder (2) in the direction of the crankshaft (3) is provided in the suction side portion of the cylinder (2), and both end surfaces of the hole are provided as the main bearing (9) and the end bearing. Closed with (10) to form a sealed space (7). Since the sealed space (7) having lower thermal conductivity than the cylinder (2) is interposed in the suction side portion of the cylinder (2), the cylinder (2) Heat transfer to the inner wall of the can be suppressed. Therefore, the temperature rise of the inner wall of the suction side portion of the cylinder (2) that has been in contact with the suction gas for a long time during the suction stroke is small, and as a result, preheating of the suction gas is suppressed.

In addition to the fixing holes, the cylinder (2), the main bearing (9), the end bearing (10), and the partition plate used between the cylinders of the two-cylinder rotary compressor, It is well known that a large number of holes are provided as a silencer or the like.
FIG. 8 is a plan view of a cylinder of a conventional two-cylinder rotary compressor.
In the conventional cylinder 108, an eccentric part 105B is fixed to the crankshaft 105, and an annular roller 112 is rotatably fitted around the eccentric part 105B.

The inner peripheral surface 108a of the cylinder 108, the outer peripheral surface 112a of the roller 112, the vane 114, and the like form a suction-side compression chamber 109s and a discharge-side compression chamber 109d.
The cylinder 108 is provided with a suction hole 108F for sucking low-pressure refrigerant, and a discharge hole 108G for discharging high-pressure refrigerant compressed in the compression chamber 109d of the cylinder 108.

As the crankshaft 105 rotates from 0 ° to 360 °, the suction-side compression chamber 109s transitions to the discharge-side compression chamber 109d, and the volume of the discharge-side compression chamber 109d decreases, thereby compressing the refrigerant. Is called.
The cylinder 108 is formed with fixing bolt holes 108A and 108B, a silencer hole 108c, a refrigerant flow path hole 108D, a work reference hole 108E, and the like.

Japanese Patent Laid-Open No. 2-140486 (FIGS. 1, 2, etc.)

However, in the configuration of the conventional Patent Document 1, the seal width of the upper and lower end surfaces of the cylinder (2) becomes narrow on the suction side where there is a pressure difference between the discharge pressure Pd and the suction pressure Ps at all times. The seal width is a thickness dimension between the inner peripheral surface and the outer peripheral surface of the cylinder (2).
For this reason, refrigerant leakage from the sealed container (1) to the compression chamber increases, and as a result, the efficiency of the compressor is lowered due to heating of the suction gas and swelling of the finger pressure. When the swelling of the finger pressure occurs, extra energy is required to compress from a high initial pressure to a discharge pressure, resulting in a reduction in compressor efficiency.

  In particular, when R32 refrigerant having high molecular weight and low molecular weight is used for R22 refrigerant and R410A refrigerant, which have been mainstream in conventional home air conditioners, the effect of leakage is further increased by rotational speed control. When performing low-speed operation, there is a concern that the influence of leakage will increase. Further, in the two-cylinder compressor, as shown in FIG. 8, there are a large number of refrigerant flow paths 108D for guiding the discharge gas from the lower compression chamber to the upper part of the compression mechanism, silencer holes 108C for silencing, etc. in the axial direction of the cylinder 108. Provided. These holes also reduce the seal width, which is a factor for reducing the sealing performance.

  The present invention has been devised in view of the above circumstances, and an object thereof is to provide a highly efficient rotary compressor in which refrigerant leakage between the sealed container and the inside of the compression chamber is reduced.

  In order to solve the above problems, a rotary compressor according to a first aspect of the present invention includes an electric motor, a crankshaft that is rotationally driven by the electric motor and provided with a compression member, and a compression in which refrigerant is compressed by the rotational driving of the compression member. A cylinder having a chamber; a main bearing that closes the cylinder in one axial direction; and a sub-bearing that closes the other in the axial direction. The cylinder, the main bearing, and the sub-bearing Has holes for fastening components in the axial direction, and all the holes extending in the axial direction other than the holes for fastening components are in a range where the crank angle of the crankshaft is 180 ° or less or 180 ° or more. Among these, it is provided on the long side where the pressure difference between the sealed container and the compression chamber becomes small.

  The rotary compressor according to the second aspect of the present invention is the rotary compressor according to the first aspect of the present invention, wherein holes having a larger area among the holes extending in the axial direction other than the holes for fastening the components are: In the crank angle of the crankshaft, the crankshaft is provided on the long side where the pressure difference between the sealed container and the compression chamber becomes small.

  A rotary compressor according to a third aspect of the present invention includes an electric motor, a crankshaft that is rotationally driven by the electric motor and provided with a compression member, and a cylinder that internally includes a compression chamber in which refrigerant is compressed by the rotational driving of the compression member. A main bearing that closes the cylinder in one axial direction and a secondary bearing that closes the other in the axial direction are provided in a sealed container, and the cylinder, the main bearing, and the secondary bearing are components in the axial direction. There is a hole for fastening, and the angular pitch of the hole for fastening the component is within a range where the crank angle of the crankshaft is 180 ° or less or 180 ° or more. Wide on the long side.

  A rotary compressor according to a fourth aspect of the present invention includes an electric motor, a crankshaft that is rotationally driven by the electric motor and provided with a compression member, and a cylinder that internally includes a compression chamber in which refrigerant is compressed by the rotational driving of the compression member. A main bearing that closes the cylinder in one axial direction and a secondary bearing that closes the other in the axial direction are provided in a sealed container, and the cylinder, the main bearing, and the secondary bearing are components in the axial direction. The angle pitch of the holes extending in the axial direction other than the holes for fastening the components has a fastening hole, and the crank angle of the crankshaft is 180 ° or less or 180 ° or more. And the pressure difference in the compression chamber is narrower on the longer time side.

  A rotary compressor according to a fifth aspect of the present invention includes an electric motor, a crank shaft that is rotationally driven by the electric motor and provided with a compression member, and a cylinder that internally includes a compression chamber in which refrigerant is compressed by the rotational driving of the compression member. A main bearing that closes the cylinder in one axial direction and a secondary bearing that closes the other in the axial direction are provided in a sealed container, and the cylinder, the main bearing, and the secondary bearing are components in the axial direction. With respect to the center of the inner diameter of the inner peripheral surface of the cylinder that has a fastening hole and forms the outer peripheral surface of the compression chamber, the center of the outer peripheral surface of the cylinder is not more than 180 ° crank angle or 180 ° In the range where the angle is greater than or equal to 0 °, the pressure difference is offset to the short side where the pressure difference between the sealed container and the compression chamber becomes small.

  A rotary compressor according to a sixth aspect of the present invention includes an electric motor, a crankshaft that is rotationally driven by the electric motor and provided with a compression member, and a cylinder that internally includes a compression chamber in which refrigerant is compressed by the rotational driving of the compression member. A main bearing that closes the cylinder in one axial direction and a secondary bearing that closes the other in the axial direction are provided in a sealed container, and the cylinder, the main bearing, and the secondary bearing are components in the axial direction. An opening area of a hole having a fastening hole and extending in the axial direction other than the part fastening hole is within the sealed container within a range in which a crank angle of the crankshaft is 180 ° or less or 180 ° or more. And the pressure difference in the compression chamber is wider on the longer side.

  A rotary compressor according to a seventh aspect of the present invention uses an R32 refrigerant as a refrigerant in the rotary compressor according to any one of the first aspect of the present invention or the third to sixth aspects of the present invention.

  The rotary compressor of the eighth aspect of the present invention is the rotary compressor according to any one of the first aspect of the present invention or the third to sixth aspects of the present invention, wherein the electric motor is controlled in rotational speed.

  ADVANTAGE OF THE INVENTION According to this invention, the highly efficient rotary compressor with which the refrigerant | coolant leak between the airtight container and the compression chamber inside is reduced is realizable.

1 is a longitudinal sectional view of a two-cylinder rotary compressor according to Embodiment 1 of the present invention. FIG. 2 is a cross-sectional view taken along the line II of FIG. 1 of the lower cylinder of the two-cylinder rotary compressor of the first embodiment. (A)-(d) is the conceptual diagram of the II cross section of FIG. 1 which shows the lower cylinder of the compression process in a rotary compressor with the pressure difference in an airtight container and a compression chamber. FIG. 5 is a plan view of a cylinder of a rotary compressor according to a second embodiment. FIG. 6 is a plan view of a cylinder of a rotary compressor according to a third embodiment. FIG. 6 is a plan view of a cylinder of a rotary compressor according to a fourth embodiment. FIG. 6 is a control block diagram of an electric motor of a rotary compressor according to a fourth embodiment. The top view of the cylinder of the conventional 2 cylinder rotary compressor. Sectional drawing of the lower cylinder which shows another example of the rotary compressor which concerns on Embodiment 1. FIG.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings as appropriate.
The present invention relates to a rotary compressor used in a refrigeration air conditioner or the like, and suppresses refrigerant leakage during a refrigerant compression process.

<< Embodiment 1 >>
FIG. 1 is a longitudinal sectional view of a high-pressure chamber type two-cylinder rotary compressor according to Embodiment 1 of the present invention. The white arrow in FIG. 1 indicates the flow path of the refrigerant.
2 is a cross-sectional view taken along the line II of FIG. 1 of the lower cylinder of the two-cylinder rotary compressor of the first embodiment. FIG. 2 shows the lower cylinder 8 as a representative of the upper cylinder 7 and the lower cylinder 8.
Hereinafter, although not shown, the upper cylinder 7 has the same configuration as the lower cylinder 8. Therefore, components having the same function are indicated by the same subscript. For example, if the reference 7A of the main bearing fastening bolt hole of the upper cylinder 7 is designated, the reference numeral of the auxiliary bearing fastening bolt hole of the lower cylinder 8 fastened by the same bolt is represented by 8A.

The rotary compressor C according to the first embodiment is a two-cylinder compressor having two cylinders 7 and 8. The upper and lower cylinders 7 and 8 each have a compression chamber 9 that sucks, compresses and discharges the refrigerant r.
The rotary compressor C compresses the refrigerants r11 and r21 sucked into the compression chambers 9 of the upper and lower cylinders 7 and 8 in the compression chambers 9 to form refrigerants r12 and r22 having a discharge pressure Pd as discharge holes 7G, It discharges in the airtight container 1 from 8G.

The compression chamber 9 of the upper cylinder 7 is formed by the outer peripheral surface 11 a of the roller 11, the inner peripheral surface 7 a of the upper cylinder 7, the main bearing 6, and the partition plate 15.
The compression chamber 9 of the lower cylinder 8 is formed by the outer peripheral surface 12 a of the roller 12, the inner peripheral surface 8 a of the lower cylinder 8, the partition plate 15, and the auxiliary bearing 10.

As shown in FIG. 1, the main bearing 6 and the sub-bearing 10 are each fixed in the sealed container 1. For example, the outer peripheral portions of the main bearing 6 and the sub-bearing 10 are fixed to the cylindrical body 1 </ b> A by welding or the like, so that the compression mechanism portion is fixed in the sealed container 1. A compression mechanism part means the component which compresses a refrigerant | coolant.
As shown in FIG. 1, the crankshaft 5 has a main bearing insertion portion 5 </ b> C inserted into the main bearing 6 in the center on one side, and a sub-bearing inserted into the sub-bearing 10 on the other end. It has a fitting portion 5D.

Then, by inserting the main bearing insertion portion 5C and the sub-bearing insertion portion 5D of the crankshaft 5 into the main bearing 6 and the sub-bearing 10, respectively, the crankshaft 5 is rotatably disposed in the sealed container 1.
The upper cylinder 7 is fastened to the main bearing 6 by main bearing fastening bolts 16. The lower cylinder 8 and the partition plate 15 are temporarily fastened to the upper cylinder 7 by positioning bolts (not shown), and then fastened to the upper cylinder 7 together with the secondary bearing 10 by secondary bearing fastening bolts 17.

A necessary amount of refrigerating machine oil (not shown) is enclosed in the sealed container 1.
A lower silencer 21 is attached to the auxiliary bearing 10 by fastening the auxiliary bearing fastening bolts 17 together. The lower silencer 21 aims to prevent the refrigerant r22 discharged from the discharge port 8G of the lower cylinder 8 from stirring the refrigerating machine oil and to mute it.
A similar upper silencer 20 is also attached to the main bearing 6.

  The rotary compressor C includes an electric element (3, 4) as a driving source, a crankshaft 5, and a compression mechanism (6, 7, 8, 10, 11, 12, 13, 14, 15) hermetically sealed. It is contained in the container 1. The compression chambers 9 of the upper and lower cylinders 7 and 8 are compressed by the power of the drive source.

The compression mechanism section includes main bearing 6, sub bearing 10, cylinders 7 and 8, eccentric parts 5A and 5B, rollers 11 and 12, vanes 13 and 14, and partition plate 15 as main elements.
The compression mechanism is connected to the electric element (4) of the drive source via the crankshaft 5.

  The sealed container 1 includes a cylindrical body 1A, a lid body 1B, and a bottom body 1C. The cylindrical body 1A is formed in a cylindrical shape using a steel plate. The lid 1B is formed in a bottomed cylindrical shape having an upper bottom plate using a steel plate. The bottom body 1C is formed in a bottomed cylindrical shape having a lower bottom plate using a steel plate.

The lid 1B and the bottom body 1C are fitted to the cylinder 1A, and the fitting portion is welded to seal the inside.
The electric element of the drive source is an electric motor, and includes a stator 3 fixed to the cylinder 1A by shrink fitting or the like, and a rotor 4 fixed to the crankshaft 5 by press fitting or the like.

The crankshaft 5 is integrally formed with eccentric portions 5A and 5B between the main bearing insertion portion 5C and the auxiliary bearing insertion portion 5D.
The annular rollers 11 and 12 are rotatably fitted in the eccentric portions 5A and 5B, respectively. Vanes 13 and 14 (see FIGS. 1 and 2) are fitted in the upper and lower cylinders 7 and 8 so as to contact the outer peripheral surfaces 11a and 12a of the rollers 11 and 12, respectively.

  The vane 13 is energized and contacts the roller 11 to divide the compression chamber 9 of the upper cylinder 7 into a suction side and a discharge side. Similarly, the vane 14 is urged to come into contact with the roller 12, thereby dividing the compression chamber 9 of the lower cylinder 8 into a suction side and a discharge side.

  With this configuration, a compression chamber 9 s on the suction side of the upper cylinder 7 is formed by the outer peripheral surface 11 a of the roller 11, the inner peripheral surface 7 a of the upper cylinder 7, the vane 13, the main bearing 6, and the partition plate 15. The compression chamber 9 d on the discharge side of the upper cylinder 7 is formed by the outer peripheral surface 11 a of the roller 11, the inner peripheral surface 7 a of the upper cylinder 7, the vane 13, the main bearing 6, and the partition plate 15. As described above, the suction-side compression chamber 9 s and the discharge-side compression chamber 9 d are partitioned by the vane 13.

  Similarly, a compression chamber 9 s on the suction side of the lower cylinder 8 is formed by the outer peripheral surface 12 a of the roller 12, the inner peripheral surface 8 a of the lower cylinder 8, the vane 14, the auxiliary bearing 10, and the partition plate 15. The compression chamber 9 d on the discharge side of the lower cylinder 8 is formed by the outer peripheral surface 12 a of the roller 12, the inner peripheral surface 8 a of the lower cylinder 8, the vane 14, the auxiliary bearing 10, and the partition plate 15. Similarly, the suction-side compression chamber 9 s and the discharge-side compression chamber 9 d are partitioned by a vane 14.

  The crankshaft 5 transmits the driving force generated by the electric elements (3, 4) of the driving source to the driven side (eccentric portions 5A, 5B, rollers 11, 12 and the like). The eccentric portions 5 </ b> A and 5 </ b> B are rotated by the crankshaft 5, whereby the compression chamber 9 is compressed and expanded via the rollers 11 and 12.

The accumulator 2 supplies refrigerant to the compression chambers 9s on the suction side of the upper and lower cylinders 7 and 8, respectively.
The accumulator 2 is coupled in front of the suction ports 22 and 23 of the compression mechanism. The refrigerants r11 and r21 sucked into the upper and lower cylinders 7 and 8 through the accumulator 2 are compressed from the suction pressure Ps to the discharge pressure Pd using the compression elements (eccentric parts 5A and 5B, rollers 11 and 12, etc.). Compressed.

The suction pressure Ps is the pressure of the refrigerants r11 and r21 at the time of suction. The discharge pressure Pd is the pressure of the refrigerants r12 and r22 when discharging from the compression chamber 9d on the discharge side.
Thereafter, the compressed refrigerants r12 and r22 are once discharged into the sealed container 1, and then flow through the sealed container 1 as indicated by the white arrows in FIG. 1, from the discharge pipe 19 installed on the lid 1B. It is discharged into a cycle such as an air conditioner.

<Refrigerant compression process>
The refrigerant compression process in the rotary compressor C is performed as follows.
Since the compression process is similarly performed in the upper and lower cylinders 7 and 8, the compression process of the lower cylinder 8 will be described, and the description of the compression process of the upper cylinder 7 will be omitted.
As shown in FIG. 2, in the lower cylinder 8, the refrigerant is surrounded by the inner peripheral surface 8 a of the lower cylinder 8, the outer peripheral surface 12 a of the roller 12, the vane 14, the partition plate 15 (see FIG. 1), and the auxiliary bearing 10. Compression is performed using the compression chamber 9 (9s, 9d) in the closed space.

FIGS. 3A to 3D are conceptual views taken along the line II of FIG. 1 showing the lower cylinder of the compression process in the rotary compressor together with the pressure difference between the sealed container and the compression chamber.
In the compression process, as shown in FIGS. 3A to 3D, one cycle of compression is performed from the crank angle 0 ° of the crankshaft 5 to the crank angle 360 ° through the crank angles 90 °, 180 °, 270 °. Done. The hatching in FIGS. 3A to 3D shows the compression chamber 9. As described above, the suction-side compression chamber 9 s and the discharge-side compression chamber 9 d are partitioned by the vanes 14.

  First, the compression process starts at a crank angle of 0 ° in FIG. At this time, the compression chamber 9s on the suction side communicates with the suction hole 8F. The refrigerant is sucked from the accumulator 2 through the suction hole 8F into the compression chamber 9s on the suction side. Therefore, the refrigerant in the compression chamber 9 has a suction pressure Ps.

When the crankshaft 5 rotates and reaches a crank angle of 90 ° in FIG. 3B, the volume of the space sandwiched between the inner peripheral surface 8a of the lower cylinder 8 and the outer peripheral surface 12a of the roller 12 is reduced, and the compression chamber on the suction side 9 s becomes a discharge-side compression chamber 9 d defined by the vane 14. The refrigerant in the discharge-side compression chamber 9d rises to the intermediate pressure Pm. The intermediate pressure Pm is a pressure between the suction pressure Ps and the discharge pressure Pd.
On the other hand, a suction side compression chamber 9s communicating with the suction hole 8F is newly formed, and the refrigerant is sucked into the compression chamber 9s from the suction hole 8F. The refrigerant in the compression chamber 9s on the suction side has a suction pressure Ps.

When the crankshaft 5 further rotates and reaches a crank angle of 180 ° in FIG. 3C, the volume of the discharge-side compression chamber 9d sandwiched between the inner peripheral surface 8a of the lower cylinder 8 and the outer peripheral surface 12a of the roller 12 further increases. It narrows. Then, the refrigerant pressure in the discharge-side compression chamber 9d increases to the intermediate pressure Pm or the discharge pressure Pd.
On the other hand, the volume of the suction side compression chamber 9 s communicating with the suction hole 8 </ b> F is expanded by the operation of the roller 12. The refrigerant in the compression chamber 9s has a suction pressure Ps.

When the crankshaft 5 further rotates and reaches a crank angle of 270 ° in FIG. 3D, the volume of the discharge-side compression chamber 9d sandwiched between the inner peripheral surface 8a of the lower cylinder 8 and the outer peripheral surface 12a of the roller 12 further increases. It narrows. Then, the refrigerant in the discharge-side compression chamber 9d rises to the discharge pressure Pd. When the refrigerant in the discharge side compression chamber 9d rises to the discharge pressure Pd, a valve (not shown) is opened and discharged into the sealed container 1 from the discharge hole 8G.
On the other hand, the volume of the suction-side compression chamber 9s communicating with the suction hole 8F is further expanded by the operation of the roller 12. The refrigerant in the compression chamber 9s has a suction pressure Ps.

When the crankshaft 5 further rotates and reaches a crank angle of 360 ° (0 °), the refrigerant having the discharge pressure Pd in the discharge-side compression chamber 9d is completely discharged into the sealed container 1 from the discharge hole 8G.
On the other hand, the volume of the suction-side compression chamber 9s communicating with the suction hole 8F is further expanded by the operation of the roller 12. As described above, the refrigerant in the compression chamber 9s has the suction pressure Ps.
The above-described one-cycle compression process with a crank angle of 0 ° to 360 ° is repeated, and the refrigerant supplied from the accumulator 2 is compressed using the compression chamber 9.

<Hole provided in the main bearing 6, the upper and lower cylinders 7, 8, the partition plate 15, and the auxiliary bearing 10>
In addition to the bolt holes 7A and 8A (see FIG. 2) through which the bolts for fastening the components are inserted, the following holes are provided in the main bearing 6, the upper and lower cylinders 7 and 8, the partition plate 15 and the auxiliary bearing 10. .
That is, a refrigerant flow path hole 8D for guiding the refrigerant discharged from the discharge port 8G of the lower cylinder 8 to the upper part of the main bearing 6, a silencer hole 8C for the purpose of silencing at a specific frequency, and a reference for processing. The machining reference hole 8E.

These holes are a contact surface between the main bearing 6 and the upper cylinder 7 which is a seal portion between the sealed container 1 and the compression chamber 9, a contact surface between the auxiliary bearing 10 and the lower cylinder 8, and the upper cylinder 7 and the middle. Since it exists on the contact surface with the partition plate 15, the contact surface between the intermediate partition plate 15 and the lower cylinder 8, etc., if excessively large holes or holes are provided with high density, the space between the sealed container 1 and the compression chamber 9 The sealing performance of the is reduced.
Therefore, from the outer space of the upper and lower cylinders 7 and 8 in the sealed container 1 with the high-pressure refrigerant (hereinafter simply referred to as the outer space in the sealed container 1) to the compression chamber 9 with the low-pressure refrigerant being compressed. This causes leakage of the refrigerant and reduces the compressor efficiency.
Then, based on the above-mentioned knowledge, the characteristic structure of the first embodiment will be described below.

As shown in FIG. 2, the coolant channel hole 8 </ b> D, the silencer hole 8 </ b> C for silencing, and the machining reference hole 8 </ b> E provided as a reference during machining all have a crank angle of 180 ° or less or 180 ° or more. Within the range, it is provided on the long side where the pressure difference between the sealed container 1 and the compression chamber 9 becomes small. That is, in the high pressure chamber system, the crank angle is set in a range of 180 ° or more. In FIG. 2, the target hole is indicated by hatching.
As described above, the crank angle of 0 ° indicates the time when the eccentric portion 5B comes to the uppermost side as shown in FIG. 3A, and the crank angle increases counterclockwise, that is, the compression process proceeds. To do.

As shown in FIG. 3C, the crank angle of 180 ° indicates the time when the eccentric portion 5B comes to the lowest side, and the crank angle of 360 ° means that the crank angle is the same as the crank angle of 0 °. Show.
That is, as shown in FIG. 2, there are holes other than the bolt holes 7A and 8A for fastening the components and the positioning bolt holes 7B and 8B in the range where the suction holes 8F having a crank angle of less than 180 ° are located on the suction side. do not do.

As shown in FIGS. 3B to 3D, in the pressure distribution in the compression chamber 9, the time during which the pressure is close to the suction pressure Ps becomes longer as the crank angle is smaller. Therefore, the refrigerant in the external space is likely to leak into the compression chamber 9 due to the pressure difference with the external space in the sealed container 1 that is the discharge pressure Pd.
In the high pressure chamber system, the external space in the sealed container 1 is always at substantially the discharge pressure Pd.

For this reason, the refrigerant flow path hole 8D, the silencing silencer hole 8C, and the processing reference hole 8E are all arranged in a range where the crank angle is 180 ° or more. As a result, the seal width in the region where the low-pressure refrigerant having a crank angle of less than 180 ° is present can be widened.
Therefore, the leakage of the refrigerant to the compression chambers 9 of the upper and lower cylinders 7 and 8 of the high-pressure refrigerant in the sealed container 1 is reduced.
As described above, the heating loss and the swelling of the finger pressure are reduced, and the compressor efficiency can be improved. Therefore, the rotary compressor C with low power consumption and high energy saving performance can be provided.

<< Embodiment 2 >>
FIG. 4 is a plan view of a cylinder of the high-pressure chamber type rotary compressor according to the second embodiment.
In the second embodiment, the rotary compressor C shown in the first embodiment has a larger diameter among the many holes such as the refrigerant flow path hole 8D, the silencer silencer hole 8C, and the processing reference hole 8E. Is provided at a position where the crank angle is large.

For example, when the holes with large diameters are in the order of the refrigerant flow path hole 8D, the silencer hole 8C for noise reduction, and the processing reference hole 8E, as shown in FIG. 4, the position where the crank angle becomes smaller from the position where the crank angle becomes larger. The refrigerant passage hole 8D, the silencing silencer hole 8C, and the processing reference hole 8E are arranged in this order.
As a result, even in the compression chamber 9, the seal width in the range of the suction side where the refrigerant is at a low pressure is long can be widened, and the leakage of the high-pressure refrigerant in the sealed container 1 into the compression chamber 9 is more effectively performed. Can be reduced.

<< Embodiment 3 >>
FIG. 5 shows a plan view of a cylinder of a high-pressure chamber type rotary compressor according to the third embodiment.
In the rotary compressor C of the third embodiment, the angle pitch of the bolt holes 7A, 8A for fastening the components is θ1 in the range of the crank angle less than 180 ° than θ3 and θ4 in the range of the crank angle of 180 ° or more. θ2 is arranged narrowly.

  Since the angular pitch θ1, θ2 of the bolt holes 7A, 8A in the range of the crank angle less than 180 ° is narrower than the angular pitch θ3, θ4 of the bolt holes 7A, 8A in the range of the crank angle of 180 ° or more, the main bearing is tightened. When the bolts 16 and the sub-bearing tightening bolts 17 are fastened, the closeness of the refrigerant on the suction side with a crank angle of less than 180 ° is higher than the closeness of the discharge side with a crank angle of 180 ° or more.

  That is, the main bearing 6, the upper cylinder 7, the partition plate 15, the lower cylinder 8, and the auxiliary bearing 10 are within a range of a crank angle of less than 180 ° where the pressure difference between the sealed container 1 and the compression chamber 9 becomes large. Adhesion between the end faces of the is improved. Thereby, the leakage of the high-pressure refrigerant in the external space in the sealed container 1 into the compression chamber 9 can be reduced. Therefore, the compressor efficiency can be improved.

<< Embodiment 4 >>
FIG. 6 is a plan view of a cylinder of the high-pressure chamber type rotary compressor according to the fourth embodiment.
In the rotary compressor C of the fourth embodiment, the center C1 of the outer peripheral surface 8b of the cylinder 8 is less than the crank angle of 180 ° with respect to the center C0 of the inner peripheral surface 8a of the lower cylinder 8 that forms the outer diameter of the compression chamber 9. The range is offset by distance ε.

  As a result, the crank angle 180 is within the range where the contact area between the main bearing 6, the upper cylinder 7 and the intermediate partition plate 15 and the contact area between the intermediate partition plate 15, the lower cylinder 8 and the auxiliary bearing 10 is less than 180 ° crank angle. It becomes larger in the radial direction than the range of not less than 360 ° and less than 360 °.

  Accordingly, the seal width on the suction side of the crank angle less than 180 ° in the range where the pressure difference between the external space in the hermetic container 1 and the compression chamber 9 becomes large is long and the crank angle is less than 360 ° and less than 360 °. It is wider than the discharge side. As shown in FIG. 6, the seal width of the lower cylinder 8 with a crank angle of 90 ° is W + 2ε with respect to the seal width W of the lower cylinder 8 with a crank angle of 270 °. That is, the seal width on the suction side can be increased by 2ε.

Therefore, leakage of the high-pressure refrigerant in the external space in the sealed container 1 into the compression chamber 9 can be reduced. Therefore, the compressor efficiency can be improved.
Therefore, improvement of the compressor efficiency can be achieved without unnecessarily increasing the volume of the parts, that is, with a configuration that suppresses the increase in cost.

<< Embodiment 5 >>
In Embodiment 5 of the present invention, R32 is used as a refrigerant in any of the rotary compressors C described in Embodiments 1 to 4.
Conventionally, when an R32 refrigerant having a high molecular weight and a low molecular weight is used for the R22 refrigerant and the R410A refrigerant, which have been mainstream in home air conditioners, the refrigerant has a higher pressure than the conventional one. According to the configuration of 4, the leakage of the refrigerant into the compression chamber 9 of the high-pressure refrigerant in the external space in the sealed container 1 can be reduced.
In the case of R32 refrigerant, since the refrigerant has a higher pressure than before, the effect of reducing refrigerant leakage can be obtained more effectively.

In FIG. 7, the control block diagram of the electric motor of the rotary compressor of Embodiment 5 is shown.
An electric motor M that is a driving source of the rotary compressor C includes an electric element stator 3 and a rotor 4.
The electric motor M is subjected to rotational speed (rotational speed) control using the control unit S shown in FIG.
The control unit S includes a microcomputer sm, a converter sa, and an inverter sb.

The microcomputer sm (hereinafter referred to as the microcomputer sm) has a storage unit such as a CPU, RDM, and RAM, and the control of the electric motor M is performed by executing a control program.
An AC voltage is supplied from the AC power source AC to the converter sa. The AC voltage is converted into a DC voltage by the converter sa, divided into the microcomputer sm and the inverter sb, and a predetermined DC voltage is supplied.

  The microcomputer sm outputs, to the inverter sb, a control signal indicating the drive voltage at the control rotation speed by the rotation speed control. The inverter sb increases or decreases the drive voltage applied to the electric motor M based on the control signal.

In the rotational speed control, when the electric motor M is operating at a low speed, the time during which the refrigerant is on the suction side of the cylinders 7 and 8 (range of crank angle less than 180 °) becomes longer. That is, in the low speed operation of the rotational speed control, the leakage of the high-pressure refrigerant in the external space in the sealed container 1 into the compression chamber 9 becomes large.
Therefore, by applying the configurations described in the first to fourth embodiments, it is possible to more effectively suppress the refrigerant leakage when performing the low speed operation in which the influence of the refrigerant leakage becomes large in the rotational speed control.

<< Other Embodiments >>
1. In the third embodiment, the angle pitch of the bolt holes 7A, 8A for fastening the components is arranged so that θ1 and θ2 in the range of crank angle less than 180 ° are narrower than θ3 and θ4 in the range of crank angle of 180 ° or more. Although the example has been described, the angular pitch of the holes other than the bolt holes 7A and 8A for connecting the components, for example, the silencer hole 8C, the refrigerant flow path hole 8D, and the machining reference hole 8EA is set to be larger than the crank angle of 180 ° or more. The angle pitch in the range of less than 180 ° may be wide. According to this configuration, since the angular pitch of the holes other than the bolt holes 7A and 8A for connecting the components in the range of the crank angle of less than 180 ° on the low pressure side of the compression chamber 9 is wide, refrigerant leakage can be suppressed.

2. Alternatively, the opening area of the holes other than the bolt holes 7A and 8A for connecting the components, for example, the silencer hole 8C, the refrigerant flow path hole 8D, and the machining reference hole 8E is 180 ° or more than the crank angle of 180 ° or less. The range may be wide. According to this configuration, since the opening area of the holes other than the bolt holes 7A and 8A for connecting the components in the range of the crank angle of less than 180 ° on the low pressure side of the compression chamber 9 is narrow, it is on the low pressure side (less than 180 ° of the crank angle). The refrigerant leakage in the region can be effectively suppressed.

3. In the first embodiment and the like, various configurations have been described. However, the configurations may be appropriately selected and combined.

4). In the above, as an embodiment of the present invention, a sealed vertical two-cylinder rotary compressor has been described as an example. However, the present invention is not limited to this, and for example, a non-sealed rotary compressor, a horizontal rotary compressor, etc. The present invention can also be applied to a rotary compressor having one or more cylinders or three cylinders or a swing compressor. The rotary compressor includes a so-called rotary compressor in which the roller 11 and the vane 13 and the roller 12 and the vane 14 are formed separately, and a so-called swing compressor and scroll compressor in which they are integrally formed. Including at least.

5. In the first embodiment and the like, the high-pressure chamber system in which the inside of the sealed container 1 has a substantially discharge pressure Pd has been described. However, the low-pressure chamber system in which the inside of the sealed container 1 has a substantially suction pressure Ps, Is also applicable to an intermediate pressure chamber system in which the suction pressure Ps and the discharge pressure Pd are intermediate. For example, in the case of the low pressure chamber system, as shown in FIG. 9, in the first embodiment, all the holes extending in the axial direction other than the component fastening holes are not more than a crank angle of 180 ° or 180 ° of the crankshaft 5. Of the above-described range, it is provided on the longer side where the pressure difference between the sealed container and the compression chamber becomes smaller, that is, the range of a crank angle of 180 ° or less. For example, in the case of a two-stage compression intermediate pressure chamber system, the first-stage compression chamber sucks in the refrigerant having the suction pressure Ps, compresses it to the intermediate pressure Pm, and discharges it into the hermetic container. Sucks the Pm refrigerant in the sealed container, compresses it to the discharge pressure Pd, and discharges it to a cycle of an air conditioner or the like. For this reason, the arrangement of holes in the first-stage compression chamber is the same as in the high-pressure chamber system, and the arrangement of holes in the second-stage compression chamber is the same as in the low-pressure chamber system.
Although Embodiment 1 was taken as an example, it is obvious that the same applies to other embodiments.

6). Of course, the main bearing tightening bolt 16 and the sub bearing tightening bolt 17 may be configured by a single bolt penetrating from the main bearing 6 to the sub bearing 10.

7). The present invention is not limited to the above-described embodiment. That is, unless otherwise specified, it is obvious that the scope of the present invention is not limited to the above-described embodiment, but merely an illustrative example.

1 Sealed container 3 Stator (electric motor)
4 Rotor (electric motor)
5 Crankshaft 5A Upper eccentric part (compression member)
5B Lower eccentric part (compression member)
6 Main bearing 7 Upper cylinder (cylinder)
8 Lower cylinder (cylinder)
7A Main bearing tightening bolt holes (holes for fastening components)
7B Positioning bolt hole (Hole for fastening parts)
7C Silencer hole (Axial hole)
7D Refrigerant channel hole (Axial hole, larger area hole)
7E Machining reference hole (Axial hole)
7G Discharge hole (Discharge hole)
8A Sub bearing tightening bolt hole (Hole for fastening parts)
8a Inner peripheral surface 8b Outer peripheral surface 8B Positioning bolt hole (Hole for component fastening)
8C Silencer hole (Axial hole)
8D Refrigerant flow path hole (Axial hole, larger area hole)
8E Machining reference hole (Axial hole)
8G discharge hole (discharge hole)
8H Vane slot 9 Compression chamber 9d Compression chamber on the discharge side (compression chamber)
10 Sub bearing 11 Upper roller (compression member)
12 Lower roller (compression member)
C Rotary compressor C0 Center of inner diameter (center of inner peripheral surface)
C1 Center of outer diameter (center of outer peripheral surface)
M motor S controller θ1, θ2, θ3, θ4 Angular pitch

Claims (8)

An electric motor,
A crankshaft that is rotationally driven by the electric motor and provided with a compression member;
A cylinder having therein a compression chamber in which the refrigerant is compressed by rotational driving of the compression member;
A main bearing that closes the cylinder in one axial direction and a secondary bearing that closes the other in the axial direction are provided in a sealed container,
The cylinder, the main bearing, and the auxiliary bearing have holes for fastening components in the axial direction,
All the axially extending holes other than the component fastening holes have a small pressure difference between the inside of the hermetic container and the compression chamber within a range where the crank angle of the crankshaft is 180 ° or less or 180 ° or more. The rotary compressor is provided on the long side. The rotary compressor according to claim 1, wherein
Of the holes extending in the axial direction, a hole having a larger area is provided on the longer side of the crank angle of the crankshaft where the pressure difference between the sealed container and the compression chamber is reduced. And rotary compressor. An electric motor,
A crankshaft that is rotationally driven by the electric motor and provided with a compression member;
A cylinder having therein a compression chamber in which the refrigerant is compressed by rotational driving of the compression member;
A main bearing that closes the cylinder in one axial direction and a secondary bearing that closes the other in the axial direction are provided in a sealed container,
The cylinder, the main bearing, and the auxiliary bearing have holes for fastening components in the axial direction,
The angular pitch of the holes for fastening the components is wide on the long side where the pressure difference between the sealed container and the compression chamber becomes small in the range where the crank angle of the crankshaft is 180 ° or less or 180 ° or more. A rotary compressor characterized by that. An electric motor,
A crankshaft that is rotationally driven by the electric motor and provided with a compression member;
A cylinder having therein a compression chamber in which the refrigerant is compressed by rotational driving of the compression member;
A main bearing that closes the cylinder in one axial direction and a secondary bearing that closes the other in the axial direction are provided in a sealed container,
The cylinder, the main bearing, and the auxiliary bearing have holes for fastening components in the axial direction,
The angular pitch of the holes extending in the axial direction other than the holes for fastening the components is such that the pressure difference between the sealed container and the compression chamber is within a range where the crank angle of the crankshaft is 180 ° or less or 180 ° or more. A rotary compressor that is narrower on the longer side of the time it gets smaller. An electric motor,
A crankshaft that is rotationally driven by the electric motor and provided with a compression member;
A cylinder having therein a compression chamber in which the refrigerant is compressed by rotational driving of the compression member;
A main bearing that closes the cylinder in one axial direction and a secondary bearing that closes the other in the axial direction are provided in a sealed container,
The cylinder, the main bearing, and the auxiliary bearing have holes for fastening components in the axial direction,
With respect to the center of the inner diameter of the inner peripheral surface of the cylinder that forms the outer peripheral surface of the compression chamber, the center of the outer peripheral surface of the cylinder is within a range where the crank angle of the crankshaft is 180 ° or less or 180 ° or more. A rotary compressor characterized in that the rotary compressor is offset to a side where the pressure difference between the sealed container and the compression chamber becomes small. An electric motor,
A crankshaft that is rotationally driven by the electric motor and provided with a compression member;
A cylinder having therein a compression chamber in which the refrigerant is compressed by rotational driving of the compression member;
A main bearing that closes the cylinder in one axial direction and a secondary bearing that closes the other in the axial direction are provided in a sealed container,
The cylinder, the main bearing, and the auxiliary bearing have holes for fastening components in the axial direction,
The opening area of the hole extending in the axial direction other than the hole for fastening the component has a pressure difference in the sealed container and the compression chamber within a range where the crank angle of the crankshaft is 180 ° or less or 180 ° or more. A rotary compressor characterized in that it is wide on the long side where it becomes smaller. In the rotary compressor as described in any one of Claim 1 or Claims 3-6,
A rotary compressor using R32 refrigerant as the refrigerant. In the rotary compressor as described in any one of Claim 1 or Claims 3-6,
The electric motor is subjected to rotational speed control.

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