JP6426645B2 - Rotary compressor - Google Patents

Description

  The present invention relates to a rotary compressor.

DESCRIPTION OF RELATED ART 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 by 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 an end bearing (10) closing both ends of the cylinder (2). And a piston (4) eccentrically rotated by a crankshaft (3) axially supported by the end bearing (10), and always in contact with the outer peripheral surface of the piston (4) The compressor (11) has a compression element (11) attached to a cylinder (2) and a motor for driving the compression element (11) housed in a closed container (1).

  In the rotary compressor, the suction side portion of the cylinder (2) is provided with a hole passing through the cylinder (2) in the direction of the crankshaft (3), and both end faces of this hole are the main bearing (9) and the end bearing Close with (10) to form an enclosed space (7). Since the closed space (7) having lower thermal conductivity than the cylinder (2) is interposed in the suction side of the cylinder (2), the gas in the closed container (1), which is hot during operation, is removed from the cylinder (2) Heat transfer to the inner wall of can be suppressed. Therefore, the temperature rise of the inner wall of the suction side portion of the cylinder (2) 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, inside the cylinder (2), the main bearing (9), the end bearing (10), and the middle partition plate used between the cylinders of the 2-cylinder rotary compressor, there are also refrigerant flow paths and noise reduction 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.

A compression chamber 109s on the suction side and a compression chamber 109d on the discharge side are formed by the inner peripheral surface 108a of the cylinder 108, the outer peripheral surface 112a of the roller 112, the vanes 114, and the like.
The cylinder 108 is provided with a suction hole 108F for sucking a low pressure refrigerant, and a discharge hole 108G for discharging a high pressure refrigerant compressed by the compression chamber 109d of the cylinder 108.

As the crankshaft 105 rotates from 0 ° to 360 °, the compression chamber 109s on the suction side transitions to the compression chamber 109d on the discharge side, and the volume of the compression chamber 109d on the discharge side decreases, thereby compressing the refrigerant. It will be.
In the cylinder 108, fixing bolt holes 108A and 108B, a silencer hole 108c, a coolant passage hole 108D, a work reference hole 108E and the like are formed.

JP-A-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) is narrowed on the suction side where the pressure difference between the discharge pressure Pd and the suction pressure Ps is always almost the same as in the closed container (1). The seal width is a thickness dimension between the inner peripheral surface and the outer peripheral surface of the cylinder (2).
For this reason, the refrigerant leakage from the inside of the closed container (1) to the compression chamber increases, and as a result, the compressor efficiency is lowered due to the heating of the suction gas and the expansion of the finger pressure. When finger pressure bulge occurs, more energy is required to compress from the high initial pressure to the discharge pressure, resulting in a decrease in compressor efficiency.

  In particular, when using a high molecular weight, low molecular weight R32 refrigerant that is high temperature / high pressure and a smaller molecular weight than the R22 refrigerant or R410A refrigerant that was mainly used in conventional home air conditioners, the influence of leakage is further increased by rotational speed control. When operating at low speed, it is feared that the influence of the leakage will increase. Furthermore, in the two-cylinder compressor, as shown in FIG. 8, there are a large number of refrigerant channels 108D for guiding the discharge gas from the lower compression chamber to the upper part of the compression mechanism, silencer holes 108C for muffling etc. in the axial direction of the cylinder 108. Provided. These holes also cause the seal width to be cut, which is a factor to reduce the sealability.

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

The rotary compressor according to the present invention comprises an electric motor, a crankshaft rotatably driven by the electric motor and provided with a compression member, a cylinder having therein a compression chamber in which a refrigerant is compressed by rotation of the compression member, and the cylinder the a sub-bearing which closes the main bearing which closes at one axial direction by the axial direction of the other in a sealed container, the cylinder, the main bearing, and the sub-bearing, the cylinder in the axial direction, the The center of the outer peripheral surface of the cylinder relative to the center of the inner diameter of the inner peripheral surface of the cylinder which has a main bearing and a part fastening hole for fastening the sub bearing and which forms the outer peripheral surface of the compression chamber In the range where the crank angle of the crankshaft is 180 ° or less or 180 ° or more, the pressure difference between the inside of the closed container and the compression chamber is offset to the side where the time difference between the inside and the compression chamber becomes small.

  According to the present invention, it is possible to realize a highly efficient rotary compressor in which refrigerant leakage in the closed container and in the compression chamber is reduced.

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 of the lower cylinder of the two-cylinder rotary compressor of Embodiment 1 taken along line II in FIG. 1; (A)-(d) is a 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. 7 is a plan view of a cylinder of a rotary compressor according to a second embodiment. FIG. 7 is a plan view of a cylinder of a rotary compressor according to a third embodiment. FIG. 10 is a plan view of a cylinder of a rotary compressor according to a fourth embodiment. The control block diagram of the motor of the rotary compressor of Embodiment 4. FIG. The top view of the cylinder of the conventional 2 cylinder rotary compressor. FIG. 7 is a cross-sectional view of a lower cylinder showing another example of the rotary compressor according to Embodiment 1.

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

<< First Embodiment >>
FIG. 1 is a longitudinal sectional view of a high-pressure chamber type two-cylinder rotary compressor according to a first embodiment of the present invention. The white arrows in FIG. 1 indicate the flow path of the refrigerant.
FIG. 2 is a cross-sectional view of the lower cylinder of the two-cylinder rotary compressor of Embodiment 1 taken along the line II in FIG. The lower cylinder 8 is shown in FIG. 2 as a representative of the upper cylinder 7 and the lower cylinder 8.
Hereinafter, although illustration is abbreviate | omitted, it is the structure similar to the lower cylinder 8 also about the upper cylinder 7. FIG. Therefore, components having the same function are indicated by the same subscript. For example, in the case of the code 7A of the main bearing tightening bolt hole of the upper cylinder 7, the code of the auxiliary bearing fastening bolt hole of the lower cylinder 8 which is tightened by the same bolt is represented by 8A.

The rotary compressor C of 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 and discharges the discharge holes 7G as refrigerants r12 and r22 of discharge pressure Pd. Exhale from inside 8G into the sealed container 1.

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 middle 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 middle partition plate 15, and the auxiliary bearing 10.

As shown in FIG. 1, the main bearing 6 and the auxiliary bearing 10 are each fixed in the closed container 1. For example, the compression mechanism portion is fixed in the sealed container 1 by fixing the outer peripheries of the main bearing 6 and the sub bearing 10 to the cylindrical body 1A by welding or the like. The compression mechanism portion refers to a component that compresses a refrigerant.
As shown in FIG. 1, the crankshaft 5 has a main bearing fitting portion 5C fitted into the main bearing 6 at the center on one side, and a sub bearing fitted into the sub bearing 10 at the other end. It has insertion part 5D.

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

A necessary amount of refrigeration oil (not shown) is enclosed in the closed container 1.
The lower silencer 21 is attached to the sub bearing 10 by co-clamping of the sub bearing tightening bolt 17. The lower silencer 21 is for the purpose of muffling that the refrigerant r22 discharged from the discharge port 8G of the lower cylinder 8 does not stir refrigeration oil.
A similar upper silencer 20 is attached to the main bearing 6 as well.

  In the rotary compressor C, the drive element motor elements (3, 4), the crankshaft 5, and the compression mechanism (6, 7, 8, 10, 11, 12, 13, 14, 15) are 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 portion is mainly composed of the main bearing 6, the sub bearing 10, the cylinders 7, 8, the eccentric portions 5A, 5B, the rollers 11, 12, the vanes 13, 14, and the middle partition plate 15.
The compression mechanism is connected to the motorized element (4) of the drive source via the crankshaft 5.

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

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

  The vanes 13 are biased and come into contact with the roller 11 to divide the compression chamber 9 of the upper cylinder 7 into the suction side and the discharge side. Similarly, the vanes 14 are biased to contact the roller 12 to divide the compression chamber 9 of the lower cylinder 8 into the suction side and the discharge side.

  With this configuration, the compression chamber 9s on the suction side of the upper cylinder 7 is formed by the outer peripheral surface 11a of the roller 11, the inner peripheral surface 7a of the upper cylinder 7, the vanes 13, the main bearing 6, and the middle 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 vanes 13, the main bearing 6, and the middle partition plate 15. As described above, the compression chamber 9s on the suction side and the compression chamber 9d on the discharge side are separated by the vanes 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 vanes 14, the auxiliary bearing 10, and the middle 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 vanes 14, the sub bearing 10, and the middle partition plate 15. Similarly, a compression chamber 9s on the suction side and a compression chamber 9d on the discharge side are separated by a vane 14.

  The crankshaft 5 transmits the driving force by the electric element (3, 4) of the driving source to the driven side (e.g., the eccentric portions 5A, 5B, the rollers 11, 12 and the like). As the eccentric portions 5A and 5B rotate by the crankshaft 5, 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, 8, respectively.
The accumulator 2 is coupled in front of the suction ports 22 and 23 of the compression mechanism unit. The refrigerants r11 and r21 respectively sucked into the upper and lower cylinders 7 and 8 through the accumulator 2 are used from the suction pressure Ps to the discharge pressure Pd using the compression elements (eccentric portions 5A, 5B, rollers 11, 12 etc.) It is 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 at the time of discharge from the compression chamber 9d on the discharge side.
Thereafter, the compressed refrigerants r12 and r22 are once discharged into the closed container 1, and then flow in the closed container 1 as shown by the white arrows in FIG. 1, and from the discharge pipe 19 installed on the lid 1B It is discharged to the cycle of an air conditioner or the like.

<Compression process of refrigerant>
The compression process of the refrigerant 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 vanes 14, the middle partition plate 15 (see FIG. 1) The compression is performed using the compression chamber 9 (9s, 9d) of the enclosed space.

Fig.3 (a)-(d) is a 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.
In the compression process, as shown in FIGS. 3A to 3D, one cycle of compression is performed from a crank angle of 0 ° of crankshaft 5 to a crank angle of 90 °, 180 °, 270 ° and a crank angle of 360 °. To be done. The hatching in FIGS. 3A to 3D indicates the compression chamber 9. As described above, the compression chamber 9 s on the suction side and the compression chamber 9 d on the discharge side are separated by the vanes 14.

  First, the start of the compression process is in the state of a crank angle of 0 ° in FIG. 3 (a). 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 into the suction side compression chamber 9s through the suction hole 8F. Therefore, the refrigerant in the compression chamber 9 has a suction pressure Ps.

When the crank shaft 5 rotates and reaches a crank angle of 90 ° in FIG. 3B, the volume of the space between the inner circumferential surface 8a of the lower cylinder 8 and the outer circumferential surface 12a of the roller 12 narrows and the compression chamber on the suction side 9s is a discharge side compression chamber 9d defined by the vanes 14. The refrigerant in the compression chamber 9d on the discharge side 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, the 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 pressure of the refrigerant in the compression chamber 9 d on the discharge side rises to the intermediate pressure Pm or the discharge pressure Pd.
On the other hand, the volume of the suction side compression chamber 9s in communication with the suction hole 8F 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 compression chamber 9 d on the discharge side rises to the discharge pressure Pd. When the refrigerant in the compression chamber 9 d on the discharge side rises to the discharge pressure Pd, a valve (not shown) is opened, and the refrigerant is discharged from the discharge hole 8 G into the closed container 1.
On the other hand, the volume of the suction side compression chamber 9s in communication 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 of the discharge pressure Pd of the compression chamber 9 d on the discharge side is completely discharged into the closed container 1 from the discharge hole 8G.
On the other hand, the volume of the suction side compression chamber 9s in communication 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 compression process of one cycle of crank angle 0 ° to 360 ° is repeated, and the refrigerant supplied from the accumulator 2 is compressed using the compression chamber 9.

<Hole provided in main bearing 6, upper and lower cylinders 7, 8, middle partition plate 15, sub bearing 10>
The main bearing 6, the upper and lower cylinders 7, 8, the middle partition plate 15, and the auxiliary bearing 10 have the following holes in addition to the bolt holes 7A, 8A (see FIG. 2) through which bolts for fastening parts are inserted. .
That is, a refrigerant passage 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 silencing of a specific frequency, and a reference at the time of processing It is the processing reference hole 8E.

These holes are contact surfaces between the main bearing 6 and the upper cylinder 7, which are seal portions between the inside of the hermetic container 1 and the compression chamber 9, contact surfaces between the sub bearing 10 and the lower cylinder 8, and the upper cylinder 7 and the middle. Because it is in the contact surface with the partition plate 15, the contact surface with the middle partition plate 15 and the lower cylinder 8, etc., if an excessively large hole or a hole is provided with a high density, the space between the inside of the sealed container 1 and the compression chamber 9 Seal performance is reduced.
Therefore, from the outer space of the upper and lower cylinders 7 and 8 in the closed vessel 1 where high pressure refrigerant exists (hereinafter simply referred to as the outer space in the closed vessel 1), to the compression chamber 9 where the low pressure refrigerant being compressed is present. And cause a reduction in the compressor efficiency.
Then, based on the above-mentioned knowledge, the characteristic structure of this Embodiment 1 is explained below.

As shown in FIG. 2, the coolant passage hole 8D, the silencer hole 8C for muffling, and the processing reference hole 8E provided as a reference during machining all have a crank angle of 180 ° or less or 180 ° or more of the crankshaft 5 It is provided on the long side of the range in which the pressure difference between the closed container 1 and the compression chamber 9 becomes smaller. That is, in the high pressure chamber system, the crank angle is arranged in the range of 180 ° or more. The target holes are hatched in FIG.
As described above, the crank angle of 0 ° refers to the time when the eccentric part 5B comes to the uppermost side as shown in FIG. 3A, and the crank angle increases counterclockwise, that is, the above-mentioned compression process proceeds Do.

As shown in FIG. 3 (c), the crank angle of 180 ° refers to the time when the eccentric part 5B comes to the lowermost side, and the crank angle of 360 ° is the same crank angle as the crank angle of 0 °. Show.
That is, as shown in FIG. 2, holes other than bolt holes 7A and 8A for fastening parts and positioning bolt holes 7B and 8B are present in the range on the suction side where suction holes 8F having a crank angle of less than 180 ° are present. do not do.

As shown in FIGS. 3B to 3D, in the pressure distribution of the compression chamber 9, the time during which the low pressure is closer to the suction pressure Ps is longer as the crank angle is smaller. Therefore, due to the pressure difference between the discharge pressure Pd and the external space in the sealed container 1, leakage of the refrigerant in the external space to the compression chamber 9 is likely to occur.
In the high pressure chamber system, the external space in the sealed container 1 is always substantially at the discharge pressure Pd.

For this reason, the refrigerant passage holes 8D, the silencer holes 8C for noise reduction, and the processing reference holes 8E are all arranged in the range where the crank angle is 180 ° or more. This makes it possible to widen the seal width in the region where there is a low pressure refrigerant in the range of a crank angle of less than 180 °.
Therefore, the leakage of the refrigerant to the compression chambers 9 of the high and low pressure refrigerant upper and lower cylinders 7 and 8 in the closed vessel 1 is reduced.
As described above, the heat loss and the swelling of the finger pressure are reduced, and the compressor efficiency can be improved. Therefore, it is possible to provide the rotary compressor C with high power saving performance with low power consumption.

<< 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, in the rotary compressor C shown in the first embodiment, a hole having a larger diameter among a large number of holes such as the refrigerant flow passage hole 8D, the silencer silencer hole 8C, and the processing reference hole 8E. In the position where the crank angle is large.

For example, when the large diameter hole is in the order of the refrigerant passage hole 8D, the silencer silencer hole 8C, and the processing reference hole 8E, as shown in FIG. , The refrigerant passage hole 8D, the silencer silencer hole 8C for noise reduction, and the processing reference hole 8E in this order.
As a result, even in the compression chamber 9, the seal width of the long suction side range where the refrigerant is at a lower pressure can be widened, and the leakage of the high pressure refrigerant in the closed container 1 into the compression chamber 9 can be made more effective. It can be reduced.

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

  The angle pitches θ1 and θ2 of the bolt holes 7A and 8A in the crank angle range of less than 180 ° are narrower than the angle pitches θ3 and θ4 of the bolt holes 7A and 8A in the crank angle range of 180 ° or more. When tightened by the bolt 16 and the sub bearing tightening bolt 17, the degree of close contact on the suction side of the refrigerant with a crank angle of less than 180 ° is higher than the degree of close contact on the discharge side with a crank angle of 180 ° or more.

  That is, the main bearing 6, the upper cylinder 7, the middle partition plate 15, the lower cylinder 8, the auxiliary bearing 10 in a range of less than 180 ° where the pressure difference between the inside of the sealed container 1 and the compression chamber 9 is large. The adhesion between the end faces of the Thereby, the leak to the compression chamber 9 of the high pressure refrigerant | coolant of the external space in the airtight container 1 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 smaller than the crank angle 180 ° with respect to the center C0 of the inner peripheral surface 8a of the lower cylinder 8 forming the outer diameter of the compression chamber 9 The range is offset by ε.

  Thereby, the contact area between the main bearing 6, the upper cylinder 7, and the middle partition plate 15 and the contact area between the middle partition plate 15, the lower cylinder 8 and the auxiliary bearing 10 have a crank angle of 180 It becomes larger in the radial direction than the range of more than 360 °.

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

Therefore, it is possible to reduce the leakage of the high pressure refrigerant in the external space in the closed container 1 into the compression chamber 9. Therefore, the compressor efficiency can be improved.
Therefore, the improvement of the compressor efficiency can be achieved without increasing the volume of parts unnecessarily, that is, with the configuration in which the increase in cost is suppressed.

<< 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.
In the case of using a high temperature, high pressure, and small molecular weight R32 refrigerant as opposed to the R22 refrigerant or R410A refrigerant that has been mainly used in domestic air conditioners, the refrigerant has a higher pressure than in the prior art. By 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 closed container 1 can be reduced.
In the case of the R32 refrigerant, since the refrigerant has a higher pressure than before, the refrigerant leakage reduction effect can be more effectively obtained.

FIG. 7 shows a control block diagram of the motor of the rotary compressor of the fifth embodiment.
The motor M of the drive source of the rotary compressor C is configured to include the stator 3 and the rotor 4 of the electric element.
The rotational speed (rotational speed) control of the electric motor M is performed 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) includes a storage unit such as a CPU, an RDM, a RAM, and the like, and the control program is executed to control the motor M.
An AC voltage is supplied from the AC power supply AC to the converter sa. The AC voltage is converted to a DC voltage by the converter sa, divided by the microcomputer sm and the inverter sb, and a predetermined DC voltage is supplied.

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

In the rotational speed control, when the 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 less than 180 ° of the crank angle) becomes long. That is, in the low speed operation of rotational speed control, the leakage of the high pressure refrigerant in the external space in the closed container 1 into the compression chamber 9 becomes large.
Therefore, by applying the configuration described in the first to fourth embodiments, it is possible to suppress the refrigerant leakage more effectively when performing the low speed operation where the influence of the refrigerant leakage becomes large in the rotational speed control.

<< Other Embodiments >>
1. In the third embodiment, the angular pitches of bolt holes 7A and 8A for fastening parts are narrowly arranged in θ1 and θ2 in a range of a crank angle less than 180 ° than θ3 and θ4 in a range of a crank angle of 180 ° or more. Although an example has been described, the angular pitch of holes other than bolt holes 7A and 8A for component connection, for example, silencer holes 8C, coolant passage holes 8D and machining reference holes 8EA, is cranked more than the range of 180 ° or more crank angle The angular 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 component connection in the range of less than the crank angle of 180 ° on the low pressure side of the compression chamber 9 is wide, refrigerant leakage can be suppressed.

2. Alternatively, the opening area of holes other than bolt holes 7A and 8A for component connection, such as silencer hole 8C, coolant passage hole 8D, and processing reference hole 8E, has a crank angle of 180 ° or more than the range of crank angle less than 180 °. The range may be wide. According to this configuration, the opening area of the holes other than the bolt holes 7A and 8A for component connection in the range of less than 180 ° of the crank angle on the low pressure side of the compression chamber 9 is narrow. The refrigerant leakage in the region can be effectively suppressed.

3. Although various configurations have been described in the first embodiment and the like, each configuration may be appropriately selected and combined.

4. In the above, as the embodiment of the present invention, in particular, the closed vertical two-cylinder rotary compressor has been described as an example, but the present invention is not limited thereto. For example, a non-closed rotary compressor, a horizontal rotary The present invention is also applicable to rotary type compressors, rotary type compressors having one or three cylinders or more, and swing compressors. Note that the rotary compressor, the roller 11 and the vane 13, and a so-called rotary compressor roller 12 and the vane 14 are configured separately, they contain at least a so-called swing compressor configured integrally.

5. In the first embodiment and the like, the high pressure chamber method in which the inside of the closed container 1 is substantially discharge pressure Pd is described, but the low pressure chamber method in which the inside of the closed container 1 is substantially suction pressure Ps It is also applicable to an intermediate pressure chamber system in which the pressure is intermediate between the suction pressure Ps and the discharge pressure Pd. For example, in the case of the low pressure chamber type, as shown in FIG. 9, in the first embodiment, all the axially extending holes other than the component fastening holes have a crank angle of 180 ° or less or 180 ° of the crank shaft 5 Among the above-mentioned range, it is provided on the long side where the pressure difference between the inside of the closed container and the compression chamber becomes small, that is, in the range of 180 ° or less of the crank angle. For example, in the case of a two-stage compression intermediate pressure chamber system, the first-stage compression chamber sucks in the refrigerant with suction pressure Ps, compresses it to the intermediate pressure Pm, and discharges it into the closed container. The refrigerant absorbs the Pm refrigerant in the closed container, compresses it to the discharge pressure Pd, and discharges it to a cycle such as an air conditioner. For this reason, the arrangement of the holes in the first-stage compression chamber is the same as the high pressure chamber system, and the arrangement of the holes in the second-stage compression chamber is the same as the low pressure chamber system.
Although Embodiment 1 is taken as an example, it is apparent that the same is true for the other embodiments.

6. Further, the main bearing tightening bolt 16 and the sub bearing tightening bolt 17 may of course be constituted by one bolt penetrating from the main bearing 6 to the sub bearing 10.

7. The invention is not limited to the embodiments described above. That is, it is also apparent that the scope of the present invention is not limited to the above-described embodiment unless stated otherwise in particular, and is merely an illustrative example.

1 Sealed container 3 Stator (motor)
4 Rotor (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 hole (hole for fastening parts)
7B Positioning bolt hole (hole for part fastening)
7C silencer hole (axial hole)
7D coolant channel hole (axial hole, larger area hole)
7E Machining reference hole (axial hole)
7G discharge hole (discharge hole)
8A Secondary bearing tightening bolt hole (hole for part fastening)
8a Inner peripheral surface 8b Outer peripheral surface 8B Positioning bolt hole (hole for fastening parts)
8C silencer hole (axial hole)
8D coolant channel hole (axial hole, larger area hole)
8E Machining reference hole (axial hole)
8G discharge hole (discharge hole)
8H Vane slot 9 Compression chamber 9d Discharge chamber (compression chamber)
10 secondary bearing 11 upper roller (compression member)
12 Lower roller (compression member)
C Rotary compressor C0 Center of inner diameter (center of inner circumferential surface)
C1 Center of outer diameter (center of outer peripheral surface)
M motor S control unit θ1, θ2, θ3, θ4 Angle pitch

Claims (1)

Electric motor,
A crankshaft rotatably driven by the motor and provided with a compression member;
A cylinder having therein a compression chamber in which a refrigerant is compressed by rotational driving of the compression member;
The sealed container is provided with 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 have holes for fastening parts for fastening the cylinder, the main bearing, and the sub bearing in the axial direction,
With respect to the center of the inner diameter of the inner peripheral surface of the cylinder forming the outer peripheral surface of the compression chamber, within the range where the center of the outer peripheral surface of the cylinder is a crank angle of 180 ° or less or 180 ° or more A rotary compressor characterized in that the pressure difference between the inside of the closed container and the inside of the compression chamber is reduced to a short time side.

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