KR100866439B1 - Rotary-type compression apparatus and refrigeration cycle apparatus using it - Google Patents

Abstract

The present invention provides a rotary compressor of high efficiency, the rotary compressor of the cylinder cylinder 12 of the one-cylinder rotary compressor (2) Dcy, the height of the cylinder (10) H, the rotary shaft (4) When the axial diameter of the eccentric part 4c is Dcr and the axial contact length of the eccentric part 4c of the rotating shaft 4 and the roller 13 is L, H / Dcy <0.4 and L / Dcr≥0.6 are It is characterized by that.

Description

ROTARY-TYPE COMPRESSION APPARATUS AND REFRIGERATION CYCLE APPARATUS USING IT}

1 is a conceptual diagram of a rotary compressor, a refrigeration cycle apparatus of a first embodiment of the present invention,

2 is a correlation diagram of H / D and refrigerant leakage in the rotary compressor of the first embodiment of the present invention;

3 is a correlation diagram of the sliding loss of the H / D and the blade of the rotary compressor of the first embodiment of the present invention,

4 is a correlation diagram of L / Dcr and crankshaft sliding loss of the rotary compressor of the first embodiment of the present invention;

5 is a longitudinal sectional view of the rotary compressor of the second embodiment of the present invention;

6 is a longitudinal sectional view of a first modification of the sub-bearing of the rotary compressor of the first embodiment of the present invention;

7 is a longitudinal sectional view of a second modification of the sub-bearing of the rotary compressor of the first embodiment of the present invention, and

Fig. 8 is a longitudinal sectional view of a modification of the compressor section of the rotary compressor of the first embodiment of the present invention.

* Explanation of symbols for the main parts of the drawings

1: rotary compressor 2: compressor unit

3: sealed case 4: rotating shaft

4a: main shaft portion 4b: minor shaft portion

4c: eccentric part 5: electric motor part

8: main bearing 9: sub-bearing

10: cylinder 12: cylinder chamber

13: roller 15: blade groove

16: blade 21: refrigeration cycle unit

22 condenser 23 expansion device

24: evaporator

The present invention relates to a rotary compressor and a refrigeration cycle apparatus using the same, and more particularly, to a rotary compressor having an improved structure of a compressor unit and a refrigeration cycle apparatus using the same.

Generally, a compressor used in an air conditioner or a refrigerator includes a rotary compressor. The rotary compressor includes a cylinder, a roller installed in the cylinder and eccentrically rotating along an eccentric portion of the rotating shaft, and a vane for partitioning the cylinder into a high pressure chamber and a low pressure chamber and reciprocating according to the eccentric rotational movement of the roller. .

On the other hand, such a rotary compressor requires high compression efficiency in order to realize energy saving, and to realize the high compression efficiency, it is necessary to improve the efficiency of the compressor unit.

In order to improve the efficiency of the compressor section, it is necessary to make a dimension in which the components forming the compression chamber of the compressor section are collected in an optimum design point.

The exclusion volume (V) of the rotary compressor is Dcy for the cylinder inner diameter, H for the cylinder height, and e for the crank eccentricity.

Obtained from the equation.

In the above formula, when the exclusion volume is constant, it is necessary to change the amount of crank eccentricity e or the cylinder inner diameter Dcy if one condition is changed, for example, the height H of the cylinder. It is difficult to see the influence of the factor.

Therefore, when the inner diameter of the cylinder is D, the cylinder height is H, and the eccentricity of the rotating shaft that gives eccentric rotation to the roller is e,

For example, a rotary compressor aimed at improving the compression efficiency has been proposed in JP-A-8-144976.

However, the rotary compressor proposed in Japanese Unexamined Patent Publication No. 8-144976 considers the range of H / D, but the correlation between the amount of refrigerant leakage from the H / D and the sealed portion, Since the correlation between the sliding loss of the H / D and the blade, the correlation between the L / Dcr (axial diameter of the eccentric portion of the rotating shaft) and the sliding loss of the crank shaft portion is not considered, there is room for improvement in the compression efficiency.

For example, in the actual product of the conventional rotary compressor, the H / Dcy and L / Dcr by the number of cylinders (1 cylinder type, 2 cylinder type) and the specification are in a predetermined range, as shown in Table 1. It is not limited.

Therefore, the present invention finds that in addition to Dcy and H, Dcr and L have a great influence on the compression efficiency of the rotary compressor, and in that the high efficiency rotary compressor can be realized by limiting the range of H / Dcy and L / Dcr. It is based.

The present invention has been made in consideration of the above-described circumstances, and an object thereof is to provide a highly efficient rotary compressor.

Moreover, it aims at providing the refrigeration cycle apparatus of high efficiency.

In order to achieve the above object, the rotary compressor according to the present invention is a one-cylinder type having one compressor mechanism including a cylinder forming a cylinder chamber and a roller which eccentrically rotates the cylinder chamber in accordance with an eccentric portion of a rotating shaft. In the rotary compressor, H / Dcy ≤ when the inner diameter of the cylinder chamber is Dcy, the height of the cylinder is H, the axial diameter of the eccentric portion of the rotating shaft is Dcr, and the contact length of the eccentric portion of the rotating shaft and the roller is L. 0.4, L / Dcr≥0.6.

The refrigeration cycle apparatus according to the present invention is characterized by comprising the compressor, the condenser, the expansion device and the evaporator.

A rotary compressor and a refrigeration cycle apparatus using the same according to the first embodiment of the present invention will be described with reference to the drawings.

1 is a conceptual diagram of a rotary compressor and a refrigeration cycle apparatus using the same according to the first embodiment of the present invention.

As shown in FIG. 1, the refrigeration cycle apparatus 21 according to the present invention communicates with the rotary compressor 1, the condenser 22, the expansion device 23, and the evaporator 24 in the first embodiment in a cycle shape. Is formed.

The rotary compressor 1 is a one-cylinder type with one rotary compression apparatus 2, accommodates the compressor part 2 in the lower part in the sealed case 3, and the compressor part 2 is equipped with the rotating shaft 4 It is comprised by accommodating the electric motor part 5 driven by the upper part.

The motor unit 5 is composed of a stator 6 which is press-fitted into the sealed case 3 and a rotor 7 accommodated in the stator 6.

The rotating shaft 4 supporting the rotor 7 has a main shaft portion 4a by the main bearing (upper bearing) 8 of the compressor portion 2, and a sub shaft portion (4) by the sub-bearing 9 (lower bearing). 4b) are respectively rotatably supported.

The main bearing 8 and the sub bearing 9 are installed so as to sandwich the cylinder (cylinder block) 10 from both sides, and fixing to the cylinder 10 is carried out by screwing the cylinder 10 with screws 11. do.

In the cylinder 10 of the compressor unit 2, a cylinder chamber 12 partitioned by a cylinder bore is formed, and the roller 13 is accommodated in the cylinder chamber 12. The roller 13 is engaged with the eccentric part 4c of the rotating shaft 4, and is eccentrically rotated while rolling the inside of the cylinder chamber 12 according to the rotational drive of the rotating shaft 4.

As for the subshaft part 4b provided in the lower part of the eccentric part 4c, the axial diameter d of this subshaft part 4b is formed smaller than the axial diameter of the rotating shaft 4 (main shaft part 4a), and The half eccentric side outer circumferential surface 4c1 of the eccentric portion 4c coincides with the outer circumferential surface 4b1 of the minor shaft portion 4b. Moreover, the thrust support member 14 which receives the thrust load of the rotating shaft 4 through the sub-shaft part 4b is provided in the lower end surface of the sub bearing 9.

In addition, the compressor unit 2 has a blade groove 15 extending radially outward from the inner circumferential surface (cylinder inner circumferential surface) of the cylinder bore, the blade 16 in the blade groove 15 to suppress the roller 13 It is urged and received by the spring 17 so that the cylinder chamber 12 is all divided into the suction side chamber and the compression side chamber which are not shown in figure.

The cylinder 10 is provided with suction ports (not shown) communicating with the suction pipe 18 on both sides of the blade groove 15, and discharge holes 19 are provided in the main bearing 8, respectively.

Next, the inner diameter Dcy of the cylinder chamber 12, the height H of the cylinder 10, the axial diameter Dcr of the eccentric portion 4c, the eccentric portion 4c, and the axial direction of the roller 13 are contacted. The correlation of length L and each dimension are demonstrated.

According to the research of the inventors etc., as shown in FIG. 2, the relationship between the H / Dcy and the leakage amount of the refrigerant in the rotary compressor having the same exclusion volume and the same eccentricity increases almost linearly as the H / Dcy increases. It can be seen that. The reason for this is that as the H / Dcy increases, the seal length between the roller and the cylinder, which is the dominant leak portion, increases, and the amount of leakage in the portion increases.

Also, as shown in FIG. 3, the relationship between the H / Dcy and the sliding loss of the blade side and the front end of the rotary compressor having the same exclusion volume and the same eccentricity is almost linearly increased as the H / Dcy increases. I can see that. The reason is that as the H / Dcy increases, the load acting on the blade side and the back increases, and the sliding loss between the blade grooves and the blade tip increases.

On the other hand, as shown in Figure 4, the relationship between the L / Dcr and the eccentric shaft sliding loss can be seen that the sliding loss increases rapidly when L / Dcr is reduced.

Specifically, the amount of leakage between the roller and the cylinder can be reduced by setting H / Dcy ≦ 0.4 as shown in FIG. 2, and by setting H / Dcy ≦ 0.4 as shown in FIG. 3, The sliding loss of the blade can be reduced, and as shown in Fig. 4, by setting L / Dcr? 0.6, the eccentric shaft sliding loss can be greatly reduced.

Based on these findings, the present invention has been completed, and the relationship with Dcy, H, Dcr, and L

It is set to. In order to improve the efficiency, the size of L / Dcr needs to be set to some extent, and when H / Dcy is made small, it is difficult to make L / Dcr large. However, according to the present invention, the efficiency of Dcy, L, and Dcr is not reduced. It is possible to set a value, to reduce the amount of leakage between the roller and the cylinder, to reduce the sliding loss of the blade and the eccentric shaft sliding loss, and to improve the efficiency of the rotary compressor.

According to the rotary compressor of the first embodiment, a highly efficient rotary compressor is realized.

Moreover, according to the refrigeration cycle apparatus which concerns on this invention, a high efficiency refrigeration cycle apparatus is realized.

Next, the rotary compressor of the second embodiment of the present invention will be described.

The second embodiment is a two-cylinder rotary compressor having two compression mechanism portions, while the first embodiment is a one-cylinder type having one compressor portion.

For example, as shown in Fig. 5, the rotary compressor 1A of the second embodiment includes two sets of compression mechanism portions 2A1 and 2A2 having the same structure through the partition member 25A.

Taking the lower compression mechanism 2A2 as an example, the inner diameter Dcy of the cylinder chamber 12, the height H of the cylinder 10, the axial diameter Dcr of the eccentric portion 4c, and the eccentric portion 4a are described. ) And each dimension of the contact length L in the axial direction of the roller 13 are set as follows.

In the rotary compressor of the second embodiment, since the cylinder 10 has two cylinders, the H relative to the Dcy is twice as large as the one cylinder type (when the cylinders have the same shape). Therefore, in order to obtain high efficiency, it is necessary to make H / Dcy smaller. However, when H / Dcy is reduced, it becomes difficult to increase L / Dcr. Therefore, in the rotary compressor of the second embodiment, H / Dcy and L / Dcr are H / Dcy ≦ 0.3 and L / Dcr≥0.5. One side is more efficient.

Other configurations are not the same as those of the rotary compressor shown in FIG. 1, and therefore the same reference numerals will be omitted.

In addition, a first modification of the sub-bearing of the first embodiment will be described.

In the first modification, the sub bearing supporting the sub bearing part of the first embodiment is a plain bearing, and a rolling bearing is provided in the sub bearing.

For example, as shown in FIG. 6, the rolling bearing 9Ba which supports the sub-shaft part 4b is provided in the sub bearing 9B of this 1st modification.

In order to satisfy H / Dcy≤0.4 and L / Dcr≥0.6, it is necessary to reduce the axial diameter Dcr of the eccentric portion 4c with respect to the load, and when the Dcr becomes small, the roller 13 is eccentric shaft. In order to engage with (4a), it is necessary to also make the axial diameter d of the sub-shaft part 4b small. When this shaft diameter d is made small, a rolling bearing tends to produce abrasion, seizure, etc., and there exists a side surface which reduces reliability. By using the rolling bearing 9Ba in the bearing of the sub-shaft 4b, it is easy to lubricate, reduces the wear coefficient, eliminates wear and seizure, and reduces the reliability even when the shaft diameter d is small. Is realized. As a rolling bearing, in addition to the ball bearing shown, a roller bearing, a needle roller bearing, etc. may be sufficient.

In addition, a second modification of the sub-bearing of the first embodiment will be described.

This second embodiment encloses a cylindrical bushing in the minor axis portion of the first embodiment.

For example, as shown in FIG. 7, the sub-bearing 9C of this 2nd modification is provided with the large diameter bearing 9Ca which supports the cylindrical bushing 4Bb externally attached to the sub-shaft 4b. In this case, after the roller 13 is engaged with the eccentric portion 4c of the rotation shaft 4, the cylindrical bushing 4Bb is mounted on the minor shaft portion 4b to adversely affect the assembling work of the roller 13. Do not give.

Thereby, substantially the same effect as having enlarged the shaft diameter of the sub-shaft part 4b is acquired, and reliability can be improved even if planar bearing 9Ca is used.

In addition, a modification of the compressor section of the first embodiment will be described.

In the present modification, the first embodiment is provided with two bearings of the main bearing and the sub bearing, and the sub bearing is removed and only the main bearing is used.

For example, as shown in FIG. 8, the compressor part 2D of this modification does not provide a subordinate shaft in the rotational shaft 4D, and does not provide the subbearing part which supports a subordinate shaft part. Instead of the sub-bearings, the cylinder chamber 12 is partitioned and a closing plate 26D that receives the thrust force of the rotational shaft 4D is provided, and the main bearing 8D is compared with the main bearing of the first embodiment. Take sufficient bearing bore and length.

This ensures reliability and makes the cantilever structure free from sub-bearings, thereby eliminating the design constraints of the shaft diameter of the sub-shaft portion, making it easy to satisfy H / Dcy≤0.4 and L / Dcr≥0.6 and to realize a highly efficient and low-cost rotary compressor. Can be.

Moreover, although the 1st modified example of the sub bearing, the 2nd modified example, and the modified example of the compressor part which removes a sub bearing are demonstrated to the rotary compressor of 1st Example as an example, it is applicable also to the rotary compressor of 2nd Example.

According to the rotary compressor according to the present invention, a highly efficient rotary compressor can be provided.

Moreover, the refrigeration cycle apparatus which concerns on this invention can provide a high efficiency refrigeration cycle apparatus.

Claims (5)

In a one-cylinder type rotary compressor provided with one compression mechanism section including a cylinder forming a cylinder chamber and a roller which eccentrically rotates the cylinder chamber in accordance with an eccentric portion of a rotating shaft. When the inner diameter of the cylinder chamber is Dcy, the height of the cylinder is H, the axial diameter of the eccentric portion of the rotating shaft is Dcr, and the contact length in the axial direction of the eccentric portion of the rotating shaft and the roller is equal to the following Equation 1 Rotary compressor. (Equation 1)

In the two-cylinder type rotary compressor provided with two compression mechanism parts which have the cylinder which forms a cylinder chamber, and the roller which eccentrically rotates in a cylinder chamber in accordance with the eccentric part of a rotating shaft, When the inner diameter of the cylinder chamber is Dcy, the height of the cylinder is H, the axial diameter of the eccentric portion of the rotating shaft is Dcr, and the contact length in the axial direction of the eccentric portion of the rotating shaft and the roller is equal to the following expression (2). Rotary compressor. (Equation 2)

The method according to claim 1 or 2, And a main bearing for supporting the main shaft of the rotary shaft and a sub-bearing for supporting the minor shaft of the rotary shaft, and having a rolling bearing between the minor shaft and the secondary bearing. The method according to claim 1 or 2, A main bearing for supporting the main shaft of the rotary shaft and a sub-bearing for supporting the minor shaft of the rotary shaft, wherein a roller is engaged with the eccentric portion of the rotary shaft, and a cylindrical bushing is provided on the minor shaft of the rotary shaft. Rotary compressor. A refrigeration cycle apparatus comprising the compressor according to any one of claims 1 to 4, further comprising a condenser, an expansion device, and an evaporator which together with the compressor form a refrigeration cycle.

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