KR20070045092A - Rotary compressor - Google Patents

Abstract

An object of the present invention is to realize a rotary compressor that is more suitable for improving energy efficiency by suppressing pressure fluctuations generated in the discharge space of an intermediate container.

The rotary compressor 1 includes a rotary low pressure side compression unit 10 for compressing a refrigerant and a rotary high pressure side compression unit 12 for compressing a refrigerant in a reverse phase with respect to the compression process of the low pressure side compression unit 10. And an intermediate container 18 in communication with the refrigerant discharge port 14 of the low pressure side compression unit 10 and the refrigerant suction port 16 of the high pressure side compression unit 12, and the intermediate container 18 has an internal container. The discharge space 20 is partitioned into the partition member 22 into the mainstream side space 20a and the semi-mainstream side space 20b, and the refrigerant discharge port 14 of the low pressure side compression section 10 is formed in the mainstream side space 20a. And the refrigerant suction port 16 of the high pressure side compression unit 12 communicate with each other, and a refrigerant passage 20c connecting the mainstream side space 20a and the semimainstream side space 20b is formed as a partition member 22. It is composed.

Refrigerant discharge port, low pressure side compression section, intermediate container, refrigerant suction port, rotary compressor

Description

Rotary compressors {ROTARY COMPRESSOR}

1 is a longitudinal sectional view showing a configuration of a rotary compressor of one embodiment to which the present invention is applied.

FIG. 2 shows the low pressure side compression section and the high pressure side compression section in FIG.

3 is a plan view of the intermediate container of FIG. 1 seen from below;

4 is a sectional view taken along the line A-A of the intermediate container of FIG.

FIG. 5 is a diagram showing a flow of a refrigerant in the discharge space of the intermediate container of FIG. 1; FIG.

6 shows the pressure amplitude of the intermediate vessel of FIG. 1 in comparison with the prior art.

FIG. 7 is a sectional view taken along the line B-B of the intermediate container of FIG. 3; FIG.

8 is a cross-sectional view taken along line C-C of the intermediate container of FIG.

9 is a sectional view taken along the line D-D of the intermediate container of FIG.

Fig. 10 is a plan view of the cover of Fig. 1 or 4;

11 is a cross-sectional view of the elastic body of FIG. 1 or FIG.

The figure which shows the measurement result of the change rate of the refrigeration cycle performance coefficient (COP) of the air conditioner of one Embodiment to which this invention is applied.

Fig. 13 is a sectional view showing another first example of intermediate container to which the present invention is applied.

Fig. 14 is a sectional view showing another second example of intermediate container to which the present invention is applied.

<Explanation of symbols for the main parts of the drawings>

1: rotary compressor

10: low pressure side compression part

12: high pressure side compression part

14: refrigerant discharge port

16: refrigerant suction port

18: intermediate container

20: discharge space

20a: mainstream space

20b: semi-mainstream space

20c: refrigerant path

22: partition member

[Document 1] Japanese Unexamined Patent Publication No. 2003-166472 (Page 10, Fig. 10)

The present invention relates to a rotary compressor applied to a refrigeration cycle device such as an air conditioner that cools indoor air.

The refrigeration cycle device represented by an air conditioner cools air, water, etc. using the refrigeration cycle which repeats the change of the state of vaporization and liquefaction of a refrigerant | coolant. As a refrigerant compressor applied to this refrigeration apparatus, a rotary two stage compressor having a two stage compression mechanism for compressing refrigerant in stages is known. For example, a rotary two stage compressor includes a rotary low pressure side compression unit for compressing a refrigerant, a rotary high pressure side compression unit for compressing a refrigerant in a reverse phase with respect to the compression process of the low pressure side compression unit, and a low pressure side compression unit. An intermediate container having an internal space (hereinafter referred to as a discharge space) in communication with the discharge port and the refrigerant suction port of the high pressure side compression section is provided.

In the intermediate container of such a rotary two-stage compressor, pressure fluctuations occur in the discharge space due to a phase difference (for example, 180 degrees) between the discharge process of the low pressure side compression unit and the suction process of the high pressure side compression unit. That is, the pressure increase due to the state in which the refrigerant discharged to the discharge space is not sucked or the pressure decrease due to the state in which suction is started before the refrigerant is discharged to the discharge space are repeated.

Therefore, in order to reduce the pressure fluctuations generated in the discharge space, the volume of the discharge space is made as large as possible. For example, the inner circumferential wall of the intermediate container is irregularly formed in the radial direction to form a petal shape, thereby avoiding the fastening member provided on the peripheral wall of the intermediate container, while actively securing the volume of the discharge space, thereby overcompressing loss in the discharge space. It is proposed to suppress this (for example, patent document 1).

[Patent Document 1]

Japanese Patent Laid-Open No. 2003-166472 (page 10, Fig. 10)

However, since the discharge space of the intermediate container is the same enlarged space without a shield, when the refrigerant is discharged in the discharge space, the pulsation component may resonate without attenuation in a certain number of operations, so the pressure fluctuation of the discharge space increases. It may become. In particular, when the specific operating speed of the compressor is high, there is a fear that the pressure fluctuation is further increased. When the pressure fluctuation is increased, energy loss is increased, such as kinetic energy resulting from the pressure fluctuation is dissipated as frictional heat in the coolant flow path wall, which causes a decrease in the refrigeration cycle performance coefficient (COP). Previous techniques such as Patent Document 1 do not consider such a pressure variation, and there is room for improvement in energy efficiency of the rotary compressor.

An object of the present invention is to realize a rotary compressor which is more suitable for suppressing pressure fluctuations in the discharge space of an intermediate container and improving energy efficiency.

In order to solve the above problems, the rotary compressor of the present invention includes a rotary low pressure side compression unit for compressing a refrigerant, a rotary high pressure side compression unit for compressing a refrigerant in an antiphase with respect to a compression process of the low pressure side compression unit, An intermediate container in communication with the refrigerant discharge port of the low pressure side compression section and the refrigerant suction port of the high pressure side compression section, wherein the intermediate container is partitioned into a partition member into at least two spaces, and the low pressure side compression in one space. And a refrigerant flow passage for communicating the refrigerant discharge port of the negative portion with the refrigerant suction port of the high-pressure side compression portion and connecting the two spaces.

That is, one space where the refrigerant discharge port of the low pressure side compression section communicates with the refrigerant suction port of the high pressure side compression section becomes a mainstream side space through which the mainstream of the refrigerant flows. In addition, another space communicating with the mainstream side space via the partition member is a semimainstream side space into which the pulsating component of the refrigerant flows in and out.

According to this, when the refrigerant is discharged from the low-pressure side compression section to the intermediate container, the mainstream of the refrigerant is drawn into the high-pressure side compression section after flowing through the mainstream side space, but part or all of the pulsating component of the refrigerant in the process is semi-mainstream side. Inflow and outflow into space. That is, the semi-mainstream space serves as a cavity resonator, that is, a shock absorber, which prevents resonance of the pulsating component of the refrigerant. As a result, resonance of the pulsating component in the discharge space can be suppressed, so that pressure fluctuations generated in the discharge space can be suppressed. As a result, energy loss due to pressure fluctuations can be reduced to improve energy efficiency.

In this case, the intermediate container includes an end plate portion having a disk shape, an outer wall portion standing up axially from the periphery of the end plate portion and partitioning the circumferential direction of the discharge space, and a cylindrical portion standing axially in the center of the end plate portion. It can be formed with a bearing and a closing plate which closes the front end side opening of the outer wall part facing the end plate part. The partition member here is a beam which is erected on the plate surface of the end plate portion from the sub-bearing to the outer circumferential wall, and the beam has a axial dimension from the end plate portion smaller than the outer wall portion to form a coolant flow path between the occluded plate. can do.

In addition, it is preferable that the sub-bearing is formed such that the outer diameter of the end plate portion is larger than the outer diameter of the tip end portion, and the partition member has an axial dimension from the end plate portion smaller than the diameter expansion portion.

In addition, the partition member includes a parallel portion parallel to the plate surface of the end plate portion, an inner circumferential side taper portion inclined toward the sub-bearing side along the axial direction from the inner circumference of the parallel portion, and an outer wall along the axial direction from the outer circumference of the parallel portion. The outer peripheral side taper part inclined to the negative side is formed in the front-end | tip part side, and a refrigerant | coolant flow path can be made into the cross section trapezoidal opening divided into the parallel part, the inner peripheral side taper part, the outer peripheral side taper part, and a blocking plate. That is, the refrigerant passage can change the opening width to a predetermined width such that the opening width gradually increases as the axial direction is directed. In other words, by adjusting the inclination angle of the inner circumferential side taper portion or the outer circumferential side taper portion, it is possible to finely adjust the size of the passage cross-sectional area of the refrigerant passage. Therefore, the pressure fluctuation can be reduced in a wide range of operating speeds, without being limited to specific operating speeds.

In addition, the intermediate container can be provided in the other space where the reinforcing beam standing up on the plate surface of the end plate part from the sub bearing to the outer peripheral wall is partitioned by the said partition member. In the reinforcing beam here, the axial dimension from the end plate portion is formed smaller than that of the partition member. Thereby, since rigidity of an intermediate container can be improved, the distortion resulting from a pressure load or the load by the fastening element at the time of assembly can be suppressed.

An embodiment of a rotary compressor to which the present invention is applied will be described with reference to the drawings. 1 is a longitudinal sectional view showing the configuration of the rotary compressor of the present embodiment. FIG. 2 is a view showing the low pressure side compression section and the high pressure side compression section in FIG. 3 is a plan view of the intermediate container of FIG. 1 seen from below. 4 is a sectional view taken along the line A-A of the intermediate container of FIG.

As shown in Fig. 1, the rotary compressor 1 applied to a refrigeration cycle apparatus such as an air conditioner has a two-stage compression mechanism for compressing refrigerant in stages. More specifically, the rotary compressor 1 applies refrigerant in a reverse phase with respect to the compression process of the rotary low pressure side compression unit 10 and the low pressure side compression unit 10 that compress the refrigerant (for example, R410A). The internal space 20 communicating with the rotary high pressure side compression unit 12 to compress, the refrigerant discharge port 14 of the low pressure side compression unit 10 and the refrigerant suction port 16 of the high pressure side compression unit 12. The intermediate | middle container 18 which has the following (discharge space 20) is provided.

Here, in the intermediate container 18 applied to the rotary compressor 1, as shown in Figs. 2 to 4, the discharge space 20 is divided into two spaces 20a and 20b as partition members 22, for example. It is partitioned. The refrigerant discharge port 14 of the low pressure side compression unit 10 and the refrigerant suction port 16 of the high pressure side compression unit 12 communicate with each other in one space 20a (hereinafter, “mainstream side space 20a”). The member 22 is formed with a coolant flow path 20c which connects the mainstream side space 20a and the other space 20b (hereinafter, semi-mainstream side space 20b).

That is, the intermediate container 18 includes a mainstream side space 20a where the refrigerant discharge port 14 of the low pressure side compression unit 10 and the refrigerant suction port 16 of the high pressure side compression unit 12 communicate with each other, and the mainstream side space. It has the semi-mainstream side space 20b partitioned through 20a and the partition member 22, The partition member 22 here is an opening which communicates the mainstream side space 20a and the semi-mainstream side space 20b. The coolant flow path 20c is formed. According to this, the semi-mainstream space 20b acts as a cavity resonator, that is, a shock absorber, which prevents resonance of the pulsating component of the refrigerant, thereby suppressing pressure fluctuations generated in the discharge space 20 to improve energy efficiency. It can increase.

In more detail, the rotary compressor 1 of this embodiment is demonstrated. As shown in Fig. 1, the rotary compressor 1 includes an electric motor 24, an end plate portion 38, a high pressure side compression unit 12, an intermediate partition plate 13, a low pressure side compression unit 10, and an intermediate container. 18 is housed in a sealed container 26. Specifically, the airtight container 26 ends in the airtight space 39 in which the electric motor 24 is arrange | positioned, and the space for rotational compression elements in which the low pressure side compression part 10, the high pressure side compression part 12, etc. are arrange | positioned. It is divided via the plate part 38. As for the rotational compression element side, the high pressure side compression part 12, the intermediate | middle partition plate 13, the low pressure side compression part 10, and the intermediate | middle container 18 are laminated | stacked axially sequentially from the electric motor 24 side, and the fastening element 15 is carried out. (For example, a bolt) is integrally fixed.

The airtight container 26 is a cylindrical body part 28, the cover part 29 of the substantially bowl shape which closes the opening by the side of the electric motor 24 of the main body part 28, and the low-pressure side of the main body part 28. The bottom part 30 which closes the opening by the side of the compression part 10 is provided. The lid 29 is provided with a discharge tube 31 through which a refrigerant compressed at high pressure Pd is discharged. In addition, for convenience of explanation, the axial direction of the main body 28 is suitably called a longitudinal direction, and the horizontal direction orthogonal to an axial direction is suitably called a horizontal direction. In addition, the direction of the cover part 29 side from the main body part 28 to the axial direction is suitably called the upper side, and the direction of the bottom part 30 side from the main body part 28 to the axial direction is suitably called the lower side.

The electric motor 24 is arrange | positioned in the airtight space 39 partitioned by the end plate part 38 in the upper side in the airtight container 26. As shown in FIG. The electric motor 24 includes a stator 32 as a stator provided annularly along the inner circumferential surface of the hermetic container 26, a rotor 34 as a rotor inserted into the stator 32 via a gap, and a rotor ( 34) is provided with a rotating shaft 36 with an upper end pivoted thereto. The rotary shaft 36 is provided with two eccentric portions, that is, an eccentric portion 42 for high compression and a low compression eccentric portion 44, on a portion on the tip end side. The eccentric part 42 here is shifted from the axial direction upward rather than the eccentric part 44, and the eccentric direction is 180 degrees in the reverse direction with respect to the eccentric part 44, for example.

The end plate portion 38 is an annular plate member fixed by welding or the like along the inner circumferential surface of the airtight container 26. This end plate part 38 is formed in the center by the cylindrical main bearing 40 which uprightly connects the rotating shaft 36 to stand up. The end plate portion 38 is provided with a discharge port 46 that penetrates in the thickness direction. The discharge plate 48 is disposed in the discharge port 46. Moreover, the discharge cover 50 is arrange | positioned in the center of the upper end surface of the end plate part 38. As shown in FIG. The discharge cover 50 is a hollow annular member surrounding the rotary shaft 36, and an internal space thereof communicates with the discharge port 46. In the discharge cover 50, a discharge port 51 is formed at a portion of the electric motor 24 side.

The high pressure side compression section 12 is interposed between the end plate portion 38 and the intermediate partition plate 13. This high-pressure side compression section 12 is located in the cylinder 52 and the substantially cylindrical cylinder 52 having a portion having an outer diameter equal to the inner diameter of the sealed container 26 as shown in Figs. A cylindrical roller 54 fitted to the outer circumference of the core portion 42 and a tip portion contact the outer circumferential surface of the roller 54 so that the cylinder 52 can be pushed back and forth with a pressing force applying means (for example, a coil spring). Supported vanes 56 and refrigerant suction ports 16 penetrating in the radial direction and communicating in the cylinder 52 are provided. The cylinder 52 here is fitted to the lower end surface of the end plate part 38 and the upper end surface of the intermediate partition plate 13, and the internal space 58 is closed. The vane 56 moves forward and backward while contacting the outer circumferential surface of the roller 54 which rotates in accordance with the eccentric motion of the eccentric portion 42, thereby partitioning the internal space 58 of the cylinder 52 into a refrigerant compression chamber and a refrigerant suction chamber. do. In addition, the refrigerant suction chamber communicates with the discharge space 20 of the intermediate container 18 via the intermediate flow path 60 connected to the refrigerant suction port 16. In addition, the refrigerant compression chamber is in communication with the sealed space 39 via the discharge port 46 formed in the end plate portion 38.

The intermediate partition plate 13 is a closed plate sandwiched between the high pressure side compression unit 12 and the low pressure side compression unit 10. This intermediate partition plate 13 has a through hole through which the rotating shaft 36 is inserted in the center. The through hole has a shaft center substantially coinciding with the axis of rotation.

The low pressure side compression section 10 is disposed between the intermediate partition plate 13 and the intermediate container 18. As shown in Figs. 1 and 2, the low pressure side compression section 10 has a substantially cylindrical cylinder 62 having a portion having an outer diameter equal to the inner diameter of the hermetic container 26, and is located in the cylinder 62. The cylindrical roller 64 fitted to the outer circumference of the core portion 44 and the tip thereof contact the outer circumferential surface of the roller 64 to be supported by the pressing force applying means (for example, a coil spring) so that the cylinder 62 can be moved forward and backward. And a refrigerant suction port 70 penetrating in the radial direction to communicate with the inside of the cylinder 62. The cylinder 62 here is fitted to the lower end surface of the intermediate partition plate 13 and the upper end surface of the intermediate container 18, and the internal space 71 is occluded. The vane 66 moves forward and backward while contacting the outer circumferential surface of the roller 64 which rotates in accordance with the eccentric motion of the eccentric portion 44, thereby partitioning the internal space 71 of the cylinder 62 into a refrigerant compression chamber and a refrigerant suction chamber. do. In the refrigerant suction chamber, gas refrigerant discharged from equipment (eg, refrigerant evaporator) of the refrigeration cycle apparatus flows through the refrigerant pipe 72 connected to the refrigerant suction port 70. The refrigerant compression chamber is in communication with the intermediate container 18.

The intermediate container 18 is a cylindrical container which temporarily stores the refrigerant discharged from the low pressure side compression section 10. More specifically, the intermediate container 18 moves downward in the center of the disk-shaped end plate portion 74 and the end plate portion 74 in contact with the lower end surface of the low pressure side compression portion 10 as shown in FIG. The cylindrical sub-bearing 43 standing up, the outer wall part 78 which protrudes downward from the peripheral part of the end plate part 74, and divides the circumferential direction of the discharge space 20, and the outer wall part 78 in the horizontal direction It is a concave-type container provided with the refrigerant | coolant discharge port 79 which penetrated. That is, the intermediate container 18 is a concave-type container opened in the reverse direction with respect to the low pressure side compression part 10 side. In addition, the end plate portion 74 is formed by passing through the refrigerant discharge port 14 communicating with the refrigerant compression chamber of the low pressure side compression portion 10 in the thickness direction. The discharge plate 80 is disposed in the refrigerant discharge port 14. In the coolant discharge port 79, an intermediate flow path 60 is formed in which the discharge space 20 communicates with the coolant suction chamber of the high-pressure side compression unit 12. The intermediate container 18 is provided with a cover 82 which is a closing plate of an annular plate that closes the opening of the lower end face.

The basic operation of the rotary compressor 1 configured as described above will be described. The arrow in FIG. 1 shows the flow of gas refrigerant as working fluid. The gas refrigerant of low pressure Ps discharged from the equipment of the refrigeration cycle apparatus (for example, the refrigerant evaporator) is sucked into the cylinder 62 of the low pressure side compression section 10 via the refrigerant pipe 72. The sucked gas refrigerant is compressed in the refrigerant compression chamber of the cylinder 62 by the eccentric rotation of the roller 64. When the pressure of the refrigerant compression chamber reaches a predetermined intermediate pressure Pm, the gas refrigerant in the refrigerant compression chamber is discharged to the discharge space 20 through the refrigerant discharge port 14 by the opening of the discharge plate 80. Since the discharge space 20 here is a space isolated in the intermediate container 18, that is, a space isolated from the sealed space 39 in the sealed container 26, the internal pressure thereof is basically a medium pressure Pm. .

The gas refrigerant discharged into the discharge space 20 is sucked into the cylinder 52 of the high pressure side compression section 12 from the refrigerant suction port 16 via the intermediate flow path 60. The sucked gas refrigerant is compressed in the refrigerant compression chamber of the cylinder 52 by the eccentric rotation of the roller 54. When the pressure of the refrigerant compression chamber reaches a predetermined high pressure Pd, the gas refrigerant in the refrigerant compression chamber is discharged from the discharge port 46 by the opening of the discharge plate 48. The discharged gas refrigerant flows out into the sealed space 39 via the discharge port 51 of the discharge cover 50. The outflowing gas refrigerant flows through the gap of the electric motor 24, and then is discharged from the discharge pipe 31 to the equipment (eg, refrigerant condenser) of the refrigeration cycle apparatus.

In the step-by-step compression process of such refrigerant, the present embodiment includes the semi-mainstream side space 20b having a cavity resonance function in the intermediate container 18, thereby discharging the low pressure side compression unit 10 and the high pressure side. Pressure fluctuations in the discharge space 20 due to the phase difference in the suction process of the compression unit 12 are reduced. In addition, although the pressure fluctuations are related to the sound velocity of the refrigerant and the amount of refrigerant pressure in the low pressure-side compression unit 10, in particular, the operating speed of the rotary compressor 1 and the volume of the discharge space 20, the present embodiment mainly deals with the refrigerant. This suppresses resonance of the refrigerant pulsating component closely related to the speed of sound.

Here, the intermediate container 18 will be described in more detail with reference to Figs. As shown in FIG. 2, in the intermediate container 18, the discharge space 20 is divided into the mainstream side space 20a and the semimainstream side space 20b via the partition member 22. As shown in FIG. The partition member 22 is provided with the refrigerant | coolant flow path 20c which is an opening which communicates the mainstream side space 20a and the semi-mainstream side space 20b. That is, the discharge space 20 is divided into the mainstream side space 20a through which the main refrigerant flows, and the semi-mainstream side space 20b through which the time-variable components of the refrigerant flow mainly. The mainstream side space 20a communicates with the semi-mainstream side space 20b over the partition member 22. In the semi-mainstream side space 20b, the coolant flows in and out through the coolant flow path 20c, and serves as a cavity type resonator.

More specifically, the intermediate container 18 is a casting member or an iron sintered member, and the end plate portion 74, the outer wall portion 78, and the sub-bearing 43 are integrally formed as shown in FIGS. 3 and 4. It is molded. That is, the intermediate container 18 is formed in the substantially concave shape by which one end surface was opened to the cover 82 side.

The end plate portion 74 is a disc on which a pedestal 84 for installing the refrigerant discharge port 14 and the discharge plate 80 of the low pressure side compression portion 10 is formed. In addition, the outer wall portion 78 is formed in a substantially cylindrical shape to partition the circumferential direction of the discharge space 20. The outer wall portion 78 has a contact surface 81 formed in parallel with the plate surface of the end plate portion 74 in contact with the cover 82. In addition, the contact surface 81 is formed by mold forming, cutting, or polishing. In addition, the outer wall portion 78 is formed with a plurality of holes (for example, four) through which the holes 86 for the fastening element 15 penetrate in the axial direction. The plurality of holes 86 are formed at equal intervals on the same circumference. Moreover, the outer wall part 78 is formed in the petal shape which made the inner peripheral wall uneven | corrugated in the radial direction. More specifically, the inner circumferential wall of the outer wall portion 78 has a portion in which the hole 86 is disposed in a concave shape in the radially inner side, and one hole 86 and another hole 86 adjacent to the hole. The part in between is formed in convex shape in radial direction outer side. By forming the inner circumferential wall of the outer wall portion 78 in the shape of a petal in this manner, the volume of the discharge space 20 can be ensured as much as possible while avoiding the hole 86. In addition, the volume of the discharge space 20 here is larger than the amount of refrigerant pressure in the low pressure side compression section 10. Therefore, overcompression loss in the discharge space 20 can be suppressed when the refrigerant is discharged from the low pressure side compression section 10 to the discharge space 20.

The sub-bearing 43 stands in a substantially cylindrical shape at the center of the end plate part 74, and is formed. The sub-bearing 43 is provided with a stepped portion on the outer diameter side, that is, the outer circumferential wall. That is, the sub-bearing 43 is formed in such a way that the outer diameter of the end plate portion 74 side is larger than the outer diameter of the cover 82 side. The stepped portion has a flat surface 88 facing the plane of the cover 82. The flat surface 88 is a recess lower than the contact surface 81 of the outer wall portion 78. The elastic body 90 is sandwiched in the gap formed between the flat surface 88 and the cover 82. In addition, the height referred to in the present embodiment is the dimension in the axial direction based on the end plate portion 74.

In addition, the sub-bearing 43 has an inner diameter at the end plate portion 74 side smaller than the inner diameter at the cover 82 side, and a stepped portion is formed. That is, the sub-bearing 43 is a contact portion 92 for journal-connecting the rotary shaft 36 is formed to the end plate portion 74 side, the non-contact portion 94 that does not journal-connect the rotary shaft 36 is covered It is formed on the (82) side. Here, the flat surface 88 formed on the outer circumferential wall of the sub-bearing 43 is located in the outer circumferential portion of the non-contact portion 94. Thereby, since the pressure load and the fixed load from the cover 82 and the elastic body 90 are absorbed by the non-contact part 94, the frictional force of the sub-bearing 43 and the rotating shaft 36 can be reduced. In addition, although the flat surface 88 is integrally formed as a part of the intermediate container 18, you may form it by machining, such as cutting.

And the intermediate | middle container 18 of this embodiment is the partition member 22 which divides the discharge space 20 into the mainstream side space 20a and the semi-mainstream side space 20b, as shown to FIG. 3, FIG. Is formed. The partition member 22 is a beam standing upright in the lower end surface of the end plate part 74 across the outer peripheral wall 78 in the radial direction from the sub bearing 43 as shown in FIG. That is, the partition member 22 is a board of substantially rectangular cross section which connects the outer wall of the sub-bearing 43 and the inner wall of the outer wall portion 78. In addition, in this embodiment, although the two beams are formed in the straight line which connects the center of the sub-bearing 43 and the center of the fastening hole 86, two or more beams are radiated from the sub-bearing 43 radially. It is good to form. In short, the discharge space 20 may be partitioned into the mainstream side space 20a and the semimainstream side space 20b by two or more beams.

As shown in Fig. 4, the partition member 22 forms a coolant flow path 20c having an approximately trapezoidal opening cross section between the cover 82. More specifically, the partition member 22 is parallel part 22a parallel to the lower end surface of the end plate part 74 at the height M lower than the contact surface 81 of the outer wall part 78, and the parallel part 22a. ) Is tapered toward the outer wall portion 78 toward the axial direction from the outer circumferential side tapered portion 22b of the sub-bearing 43 side and the axial direction from the outer circumference of the parallel portion 22a. The photo outer peripheral side taper part 22c is formed in the front-end | tip part side. The inner peripheral side taper part 22b here is an inclined surface which connects the inner peripheral edge of the parallel part 22a, and the outer peripheral edge of the flat surface 88. As shown in FIG. Moreover, the outer peripheral side taper part 22c is an inclined surface which connects the outer peripheral edge of the parallel part 22a to the inner peripheral edge of the outer wall part 78. As shown in FIG. That is, the space divided by the parallel part 22a, the inner peripheral taper part 22b, the outer peripheral taper part 22c, and the cover 82 becomes the refrigerant | coolant flow path 20c. Incidentally, the inclination angles of the inner circumferential side tapered portion 22b and the outer circumferential side tapered portion 22c here are 45 degrees with respect to the rotation axis 36, but can be changed as necessary. That is, when adjustment of the flow path cross-sectional area S of the refrigerant | coolant flow path 20c is needed, the height of the parallel part 22a and the inclination angle of the inner peripheral side taper part 22b and the outer peripheral side taper part 22c may be changed.

FIG. 5 is a diagram showing the flow of the refrigerant in the discharge space 20 of the intermediate container 18 of FIG. As shown in Fig. 5, when gas refrigerant is discharged from the low pressure side compression section 10 through the refrigerant discharge port 14 to the intermediate container 18, the mainstream of the refrigerant flows through the mainstream side space 20a and then the refrigerant. While being sucked into the high-pressure side compression section 12 via the outlet 79, some or all of the pulsating component of the refrigerant, that is, the refrigerant fluctuation component, flows in and out of the semi-mainstream space 20b. In other words, the semi-mainstream space 20b serves as a cavity resonator, that is, a shock absorber, which prevents resonance of the pulsating component of the refrigerant. Thereby, since resonance of the pulsation component in the discharge space 20 can be suppressed, increase in the pressure fluctuations generated in the discharge space 20 is suppressed. As a result, energy loss due to pressure fluctuation can be reduced and energy efficiency can be improved.

In other words, since the discharge space 20 has a semi-mainstream side space 20b which serves as a cavity resonator with the coolant flow path 20c as a boundary, the discharge space 20 has a medium pressure Pm generated in the discharge space 20. Pressure fluctuations are suppressed.

6 is a diagram showing the pressure amplitude of the intermediate container 18 of the present embodiment in comparison with the prior art. 6, the horizontal axis represents the operating speed min- ¹ of the rotary compressor 1, and the vertical axis represents the pressure amplitude MPa of the intermediate container 18 with respect to the operating speed. As shown in Fig. 6, the pressure amplitude increases as the operating rotation speed increases from the lowest rotation speed. In the prior art, the operating amplitude is maximum, for example, in the range of 4000 (min ⁻¹ ) to 6000 (min ⁻¹ ). That is, since the range of the general operation speed is, for example, 1000 (min ^-1 ) to 8000 (min ^-1 ), it can be seen that the pressure amplitude increases in the relatively high speed rotation in the prior art. In this respect, according to the present embodiment, since the maximum value of the pressure amplitude on the high speed rotation side can be reduced, the refrigeration cycle performance coefficient (COP) is improved and the noise and vibration generated by the rotary compressor 1 are suppressed.

In addition, according to the present embodiment, the opening width of the refrigerant flow path 20c is gradually increased as the opening width of the refrigerant flow path 20c is changed in the axial direction. Therefore, the opening width of the refrigerant flow path 20c is not limited to a constant operating speed (frequency). Pressure fluctuations can be reduced in the operating speed. More specifically, regarding the intermediate container 18 of this embodiment, the height N of the parallel part 22a of the partition member 22 is changed, or the inner peripheral side taper part 22b and the outer peripheral side taper are changed. By changing the inclination angle of the part 22c, the magnitude | size of the flow path cross section area S of the refrigerant | coolant flow path 20c can be finely adjusted. For example, when the flow path cross-sectional area S is reduced, the resonance function of the semi-mainstream side space 20b is exhibited in the range on the high speed rotation side. Moreover, when the flow path cross-sectional area S is increased, the resonance function of the semi-mainstream side space 20b is exhibited in the range of the low rotation side. However, if the flow path cross-sectional area S is excessively increased, the discharge space 20 becomes substantially the same as the previously enlarged conventional space, so that the resonance function is not exerted and the pressure fluctuation may not be sufficiently suppressed. Therefore, about the magnitude | size of the flow path cross-sectional area S, it is desirable to set it as the predetermined area or more. The appropriate value of the flow path cross-sectional area S can be obtained, for example, from actual measurements.

In the intermediate container 18 of the present embodiment, as shown in Figs. 3 and 4, a second beam 96 as a reinforcing member is provided in the semi-mainstream space 20b. The beam 96 is similar to the partition member 22 in that it is integrally formed on the lower end face of the end plate portion 74 from the sub-bearing 43 over the outer circumferential wall 78 in the radial direction, but the partition member 22 It differs in that it has a parallel plane of height L lower than the height N of the parallel planes 22a. By providing such a beam 96, since the rigidity of the intermediate container 18 can be improved, the deformation resulting from the pressure load or the load by the fastening element 15 at the time of assembly can be suppressed.

In addition, the intermediate container 18 is demonstrated. FIG. 7 is a sectional view taken along the line B-B of the intermediate container of FIG. 7 is a diagram showing the shape of the partition member 22 in the B-B cross section. As shown in Fig. 7, the partition member 22 is formed with a wide end at the base portion toward the end plate portion 74. As shown in Figs. That is, in the partition member 22, the leg part 98 as a reinforcement member is formed in the engagement part with the end plate part 74. As shown in FIG. This ensures the rigidity of the partition member 22 even when the thickness of the partition member 22, that is, the length of the flow path of the coolant flow path 20c is shortened to reduce the frictional loss.

8 is a cross-sectional view taken along line C-C of the intermediate container of FIG. Fig. 8 shows the shape of the beam 96 in the C-C cross section. As shown in Fig. 8, the beam 96 has a wide end at the base as it faces the end plate 74. As shown in Figs. That is, in the beam 96, the leg part 100 as a reinforcement member is formed in the engagement part with the end plate part 74. As shown in FIG. This makes it possible to secure the rigidity of the beam 96 even when the thickness of the beam 96 is reduced to reduce the refrigerant ventilation resistance of the semi-mainstream side space 20b, thereby reducing the deformation of the intermediate container 18. Can be.

9 is a sectional view taken along the line D-D of the intermediate container of FIG. That is, FIG. 9 shows the height M of the contact surface 81 of the outer wall portion 78, the height N of the parallel portion 22a of the partition member 22, and the height L of the beam 96. The relationship is shown. As shown in Fig. 9, the flow path cross-sectional area S of the coolant flow path 20c is secured by making the height N of the parallel portion 22a shorter than the height M of the contact surface 81. Further, by making the height L of the beam 96 shorter than the height N of the parallel portion 22a, the volume V of the semi-mainstream side space 20b is secured while improving the rigidity of the intermediate container 18. can do.

10 is a plan view of the cover 82 of FIG. 1 or 4. As shown in Fig. 10, the cover 82 is a disk-shaped member punched and formed by press working. The cover 82 has a plurality of holes (for example, four) formed through the holes 102 for the fastening element 15 in the plate thickness direction. The plurality of holes 102 are formed at equal intervals on the same circumference and correspond to the position and number of the holes 86 of the intermediate container 18. In addition, the cover 82 is formed with a hole 104 penetrating in the plate thickness direction in the center of the plate surface. This hole 104 is for passing the tip portion of the non-contact portion 94 of the sub-bearing 40. More specifically, the hole 104 is formed in the same diameter as the outer diameter of the non-contact portion 94 of the sub-bearing 40, as shown in Figs. That is, the non-contact portion 94 and the cover 82 are joined by inserting the tip portion of the non-contact portion 94 into the hole 104. Then, the sealing surface is formed by inserting the elastic body 90 into the gap between the cover 82 and the flat surface 88.

11 is a cross-sectional view of the elastic body 90 of FIG. As shown in Fig. 11, the elastic body 90 is a substantially annular conical disc spring formed by pressing the copper member. As shown in FIG. 4, this elastic body 90 is arrange | positioned at the flat surface 88 along the outer periphery of the front-end | tip part of the sub-bearing 40. As shown in FIG. That is, the elastic body 90 is fitted in the gap between the flat surface 88 and the cover 82. When arranging the elastic body 90, the bottom surface of the elastic body 90 comes into contact with the plane of the cover 82. As the elastic body 90, a disk-shaped gasket, an O-ring, or the like can be used. However, when using a gasket, it is good to apply the rubber material or resin material which is easy to deform | transform.

12 is a diagram showing measurement results of the rate of change of the refrigeration cycle performance coefficient COP when the flow path cross-sectional area S of the coolant flow path 20c is controlled. 12 represents the ratio (S / V) of the volume [V (mm)] of the semi-mainstream side space 20b to the flow path cross-sectional area [S (mm 2)] of the coolant flow path 20c. The vertical axis | shaft has shown the change rate (%) of COP of an air conditioner with respect to ratio (S / V). In addition, COP here is the harmonic power of the air conditioner divided by the input. In addition, relative evaluation was performed based on the COP when the ratio (S / V) was zero.

As shown in Fig. 12, the rate of change of the COP of the air conditioner rapidly increased as the ratio (S / V) increased from zero, and gradually decreased on the basis of the constant ratio (S / V). That is, the initial increase in the ratio S / V from zero increases the amount of refrigerant passing through the flow path cross-sectional area S (mm 2) with the increase in the ratio S / V, so that the resonance of the semi-mainstream side space 20b is resonated. Since the function is exerted, the pressure fluctuation of the discharge space 20 is suppressed, and as a result, the COP of the air conditioner is improved. However, when the ratio S / V is excessively increased beyond a predetermined value, the division between the semi-mainstream side space 20b and the mainstream side space 20a becomes ambiguous, so that the discharge space 20 is similarly expanded. Since it becomes substantially the same as a space, the pressure fluctuation of the discharge space 20 cannot fully be suppressed, and COP of an air conditioner is reduced. In addition, as the ratio S / V increases, the effect of improving the rigidity of the end plate portion 74 by the partition member 22 decreases, so that the mechanical loss due to deformation of the end plate portion 74 increases. In light of these circumstances, the ratio (S / V) of the present embodiment is, for example, 0.1 × 10 ⁻² (mm ⁻¹ ) as the lower limit, and for example, 2.0 × 10 ⁻² (mm ⁻¹ ) is the upper limit. It is preferable to exist in the range made into. If it exists in the range, for example, 1% or more of COP improvement effect which is a measurement error range of the performance measuring apparatus of a general air conditioner can be acquired.

As mentioned above, although one Embodiment of the rotary compressor 1 which applied this invention was described, it is not limited to this.

13 is a sectional view showing another first example of the intermediate container 18 of the present embodiment. As shown in Fig. 13, the intermediate container 18 of the present example has a flat surface 88 on the outer circumferential wall of the sub-bearing 43 in that the outer circumferential wall of the sub-bearing 106 is formed with the same diameter in the axial direction. It differs from the form of FIG. 4 in which the stepped part is provided. That is, the intermediate | middle container 18 of this example adjusts the height of the flat surface 88 of FIG. 4 to the connection surface 81. As shown in FIG. Accordingly, the sub-bearing 106 has an outer circumference of its lower end surface 108 in contact with the plane of the cover 82. The partition member 22 here connects the parallel part 22a which is lower than the lower end surface 108 of the sub-bearing 106, and the inner periphery of the parallel part 22a to the outer periphery of the lower end surface 108. FIG. The inner peripheral side taper part 22g and the outer peripheral side taper part 22c which connect the outer peripheral edge of the parallel part 22a with the inner peripheral edge of the outer wall part 78 are formed. Thereby, the flow path cross-sectional area S of the refrigerant | coolant flow path 20c formed between the partition member 22 and the plane of the cover 82 can be ensured. Moreover, although the inclination angle of the inner peripheral taper part 22g is larger than the outer peripheral taper part 22c, it is not limited to this, What is necessary is just to adjust it as needed.

14 is a sectional view showing another second example of the intermediate container of the present embodiment. As shown in Fig. 14, in the intermediate container 18 of this example, the refrigerant passage 20c is formed in the entire region of the partition member 22 in that the refrigerant passage 20c is formed in a part of the partition member 22. It is different from the form of 13. That is, in the intermediate container 18 of this example, since the width | variety of the refrigerant | coolant flow path 20c is smaller than the partition member 22, the width | variety of the refrigerant | coolant flow path 20c differs from the form of FIG. 12 same as the partition member 22. As shown in FIG. In other words, the partition member 22 has the outer periphery of its distal end face in contact with the plane of the cover 82. The partition member 22 here connects the parallel part 22a which is lower than the lower end surface 108 of the sub-bearing 106, and the inner periphery of the parallel part 22a to the outer periphery of the lower end surface 108. As shown in FIG. 22 g of inner peripheral side taper parts and the outer peripheral side taper part 22h which inclined toward the cover 82 from the outer periphery of the parallel part 22a are formed. Thereby, since the rigidity of the partition member 22 becomes high, the rigidity of the intermediate container 18 improves as a result.

As described above, according to the present embodiment, since the pressure pulsation of the intermediate pressure Pm in the intermediate container 18 is suppressed by providing the cavity type resonance function in the intermediate container 18, the freezing cycle performance coefficient COP is improved. The noise and vibration generated in the rotary compressor 1 can be suppressed.

According to the present invention, it is possible to realize a rotary compressor more suitable for improving energy efficiency by suppressing pressure fluctuations generated in the discharge space of the intermediate container.

Claims (5)

A rotary low pressure side compression unit for compressing the refrigerant, a rotary high pressure side compression unit for compressing the refrigerant at an inverse phase with respect to the compression process of the low pressure side compression unit, a refrigerant discharge port of the low pressure side compression unit, and the high pressure side compression unit In a rotary compressor having an intermediate container in communication with a refrigerant suction port, The intermediate container has an internal space partitioned into at least two spaces by a partition member, the refrigerant discharge port of the low pressure side compression section and the refrigerant suction port of the high pressure side compression section communicate with one space by providing the two spaces with the partition member. A rotary compressor characterized by forming a refrigerant passage to be connected. The said intermediate container is an end plate part of a disk shape, the outer wall part which stands up axially from the periphery of the said end plate part, and partitions the circumferential direction of the said discharge space, and the axial direction in the center of the said end plate part. It has a cylindrical sub-bearing which has stood up, and a closing plate which closes the tip side opening of the outer wall part in the face of the end plate part, and the partition member stands on the plate surface of the end plate part from the sub bearing to the outer circumferential wall. The beam is provided, wherein the beam has a axial dimension from the end plate portion smaller than the outer wall portion, and forms the refrigerant passage between the closure plate. 3. The said sub-bearing is formed so that the outer diameter of the said end plate part may expand diameter more than the outer diameter of the tip part side, and the said partition member is smaller in the axial dimension from the said end plate part than the said diameter expansion part. Rotary compressor. The said partition member is a parallel part parallel to the plate surface of the said end plate part, The inner peripheral side taper part inclined toward the said sub bearing side as it goes to the axial direction from the inner periphery of the said parallel part, An outer circumferential side taper portion inclined toward the outer wall portion side is formed on the distal end side as it goes from the outer circumference of the parallel portion to the axial direction, and the refrigerant flow path includes the parallel portion, the inner circumferential side taper portion, and the outer circumferential side taper portion. And a trapezoidal opening in the section partitioned by the occlusion plate. The reinforcement beam according to claim 2 or 3, wherein the intermediate container is provided in the other space partitioned by the partition member, and a reinforcing beam erected on the plate surface of the end plate portion from the sub-bearing to the outer circumferential wall. And said reinforcing beam is smaller in axial dimension from said end plate portion than said partition member.

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