CN103711699B

CN103711699B - Rotary compressor

Info

Publication number: CN103711699B
Application number: CN201310459340.6A
Authority: CN
Inventors: 谷真男; 加藤太郎; 浮冈元一; 新井聪经; 五前尚久; 佐藤幸一
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2012-10-01
Filing date: 2013-09-25
Publication date: 2016-05-11
Anticipated expiration: 2033-09-25
Also published as: JP5766165B2; CN103711699A; CN203488374U; JP2014070619A; CZ306348B6; KR101539853B1; KR20140043287A; CZ2013722A3

Abstract

The sealing the invention provides between space, high-pressure side and the low-pressure side space that can prevent in cylinder chamber reduces the rotary compressor that also can increase the discharge capacity of rotary compressor. Rotary compressor (100) has compression mechanical part. This compression mechanical part have the eccentric part (4c) that is arranged on sliding freely crank axle (4) piston (20), be formed with cylinder chamber cylindraceous and in this cylinder chamber, configuring eccentric part (4c) and the cylinder (7) of piston (20) and by above-mentioned cylinder chamber in be separated into the blade (9) of low-voltage space and high-pressure space. In addition, piston (20) by be located at sliding freely eccentric part (4c) outer peripheral face inner circumferential side piston (21) and be located at inner circumferential side piston (21) outer peripheral face outer circumferential side piston (22) form. Inner circumferential side piston (21) is dividing in the cut multiple arc-shaped parts of section (21a) along the central shaft of eccentric part (4c).

Description

Rotary compressor

Technical field

The present invention relates to rotary compressor kind of refrigeration cycle, that carry out the compression of refrigerant gas for the refrigerating air conditioning device such as air conditioner, refrigerator.

Background technology

The piston that proposes before to have following rotary compressor (rotary compressor), this rotary compressor to there is the eccentric part that is arranged on sliding freely crank axle, formed cylinder in this cylinder chamber of cylindric cylinder chamber and above-mentioned cylinder configuration and by cylinder chamber in be separated into the blade of low-voltage space and high-pressure space. In this rotary compressor, the space of being divided by cylinder chamber's inner peripheral surface, piston outer peripheral face and blade is discharge chambe, and piston is done eccentric rotary motion in cylinder chamber, thereby by the refrigerant compression being drawn in cylinder chamber. In this rotary compressor before, also propose to have the compressor that piston is divided into multiple parts.

For example, piston being divided in the rotary compressor before of multiple parts, as the structure that has realized the wearing and tearing that prevent the piston outer peripheral face causing because of the slip of blade and piston outer peripheral face, the scheme of " piston of rotary compressor is become to the 1st cylinder 16a in outside and the such duplex of the 2nd cylinder 16b of inner side, and the hole 24 that the inner face of above-mentioned the 2nd cylinder 16b is communicated with outside is set " has been proposed. (referring to patent documentation 1).

Prior art document

Patent documentation

Patent documentation 1: Japanese kokai publication hei 5-256282 communique (summary, Fig. 1,2)

Summary of the invention

In the rotary compressor of recording at patent documentation 1, the inner circumferential side piston (being recited as the 2nd cylinder 16b in patent documentation 1) that is arranged on sliding freely eccentric part is to be shaped with columnar overall thing. This inner circumferential side piston is that main shaft or the countershaft of the crank axle adjacent at handle and eccentric part is arranged on eccentric part through after the piston of inner circumferential side. Therefore, the rotary compressor pattern of wants that patent documentation 1 is recorded is, the outer peripheral face of the anti-eccentric side of eccentric part (eccentric part, with the outer peripheral face of eccentric direction opposition side) is more outstanding than the outer peripheral face of main shaft or countershaft. Or, the outer peripheral face of the outer peripheral face of the anti-eccentric side of eccentric part and main shaft or countershaft need to be formed as to the same face.

; as shown in Figure 7 (a); if when the offset (distance between the central shaft of the central shaft of main shaft 4a and countershaft 4b and eccentric part 4c) that the radius of eccentric part 4c is Re, eccentric part 4c is e, be Re-e from the central shaft of main shaft 4a and countershaft 4b to the distance the outer peripheral face of the anti-eccentric side of eccentric part 4c. Therefore, the rotary compressor that patent documentation 1 is recorded, inner circumferential side piston 50 when main shaft 4a side is installed to eccentric part 4c, be Rm if establish the radius of main shaft 4a, must meet Re-e >=Rm and form crank axle 4. In addition, the rotary compressor that patent documentation 1 is recorded, inner circumferential side piston 50 when countershaft 4b side is installed to eccentric part 4c, be Ra if establish the radius of countershaft 4b, must meet Re-e >=Ra and form crank axle 4.

Its reason is, as shown in Figure 7 (b) shows, if the outer peripheral face of the anti-eccentric side of eccentric part 4c than the outer peripheral face of main shaft 4a or countershaft 4b recessed (that is, and inner circumferential side piston 50 when main shaft 4a side is installed to eccentric part 4c, Re-e < Rm; Inner circumferential side piston 50 when countershaft 4b side is installed to eccentric part 4c, Re-e < Ra),, in the time will inner circumferential side piston 50 being installed on eccentric part 4c, eccentric part 4c and inner circumferential side piston 50 interfere, thereby inner circumferential side piston 50 can not be installed on eccentric part 4c.

On the other hand, while wanting to expand discharge capacity in order to increase the ability (high output) of rotary compressor, must in the expansion that suppresses piston external diameter, increase the offset (with respect to the main shaft of crank axle and the offset of countershaft) of piston. That is to say, while wanting to expand discharge capacity in order to increase the ability (high output) of rotary compressor, must in the expansion that suppresses eccentric part external diameter, increase the offset (with respect to the main shaft of crank axle and the offset of countershaft) of eccentric part. Increase the offset of eccentric part in the expansion that suppresses eccentric part external diameter time, the outer peripheral face of the anti-eccentric side of eccentric part 4c becomes the state more recessed than the outer peripheral face of main shaft 4a or countershaft 4b (, becoming the state of Re-e < Rm or Re-e < Ra).

But as shown in Figure 7, the rotary compressor that patent documentation 1 is recorded, if the relation between the outer peripheral face of the outer peripheral face of the anti-eccentric side of eccentric part and main shaft or countershaft is not Re-e >=Rm or Re-e >=Ra, just can not be installed to piston on eccentric part. Therefore, the rotary compressor that patent documentation 1 is recorded, the problem existing is, the outer peripheral face that the degree that increases the offset of eccentric part in the expansion that suppresses eccentric part external diameter can not reach the anti-eccentric side that makes eccentric part 4c becomes the recessed state of outer peripheral face than main shaft 4a or countershaft 4b, so, there is boundary for the ability increase of rotary compressor.

At this, as the method for discharge capacity that expands rotary compressor, also considered eccentric part and piston offset to remain unchanged and the method for increasing the height of piston and cylinder. But, between the outer peripheral face (outer peripheral face of the eccentric direction side of eccentric part) and cylinder chamber's inner peripheral surface of the eccentric side of piston, be the sealing that is divided into low-voltage space and high-pressure space in cylinder chamber. Therefore,, if increase the height of piston and cylinder, the length of sealing portion just increases. Therefore, while increasing by the ability that the method for height of increasing piston and cylinder realizes rotary compressor, the refrigerant gas of high-pressure space side can leak to low-voltage space side, the weight flow that is drawn into the refrigerant gas of (in cylinder chamber) in discharge chambe reduces, thereby has the significantly reduced problem of efficiency of rotary compressor.

The present invention makes in order to address the above problem, and its objective is that the sealing providing between space, high-pressure side and the low-pressure side space that can prevent in cylinder chamber reduces and can increase the rotary compressor of the discharge capacity of rotary compressor.

Rotary compressor of the present invention, has: motor, and this motor has stator and rotor; Crank axle, this crank axle is by above-mentioned Motor Drive, have be fixed on above-mentioned rotor main shaft, be located at above-mentioned main shaft axial opposition side countershaft and be formed on above-mentioned main shaft and above-mentioned countershaft between eccentric part; Compression mechanical part, this compression mechanical part has the piston that is installed on sliding freely above-mentioned eccentric part, is formed with cylinder chamber cylindraceous and in this cylinder chamber, is configuring the cylinder of above-mentioned eccentric part and above-mentioned piston and will in above-mentioned cylinder chamber, be separated into the blade of low-voltage space and high-pressure space; And closed container, this closed container is accommodated above-mentioned motor, above-mentioned crank axle and above-mentioned compressor structure portion; Wherein, above-mentioned piston is made up of with the outer circumferential side piston of the outer peripheral face that is located at this inner circumferential side piston the inner circumferential side piston of the outer peripheral face that is located at sliding freely above-mentioned eccentric part; Above-mentioned inner circumferential side piston is made up of multiple arc-shaped parts.

In rotary compressor of the present invention, piston is made up of with the outer circumferential side piston of the outer peripheral face that is located at this inner circumferential side piston the inner circumferential side piston of the outer peripheral face that is located at sliding freely eccentric part. In addition, inner circumferential side piston is made up of multiple arc-shaped parts. Therefore, rotary compressor of the present invention can sandwich eccentric part with multiple arc-shaped parts (from the direction vertical with the central shaft of eccentric part) each arc-shaped part is installed is inner circumferential side piston. Therefore,, even if crank axle becomes the outer peripheral face structure more recessed than the outer peripheral face of main shaft or countershaft of the anti-eccentric side of eccentric part, also inner circumferential side piston can be arranged on eccentric shaft. Therefore, rotary compressor of the present invention is not increased the height of piston and cylinder, just can increase discharge capacity.

, rotary compressor of the present invention can not cause the remarkable reduction of the efficiency being produced by the refrigrant leakage at the sealing place between piston and cylinder chamber's inner peripheral surface, can increase discharge capacity. In other words, rotary compressor of the present invention, in the time not changing discharge capacity, can reduce than rotary compressor before the height of piston and cylinder, more can suppress the refrigrant leakage at the sealing place between the indoor side face of piston and cylinder than rotary compressor before.

Therefore, can provide can be than the rotary compressor of high output, high efficiency more before in the present invention.

Brief description of the drawings

Fig. 1 is the longitudinal section that represents the rotary compressor of embodiment of the present invention.

Fig. 2 is the sectional elevation that represents the compression mechanical part of the rotary compressor of embodiment of the present invention.

Fig. 3 is the key diagram of the inner circumferential side piston of the rotary compressor for embodiment of the present invention is described, is (a) longitudinal section that represents crank axle and inner circumferential side piston, (b) is the top view that represents inner circumferential side piston.

Fig. 4 is figure rotary compressor, that piston is installed to the method for eccentric part for embodiment of the present invention is described, is the stereogram that represents inner circumferential side piston to be assembled into the state before the eccentric part of crank axle.

Fig. 5 is figure rotary compressor, that piston is installed to the method on eccentric part for embodiment of the present invention is described, is to represent inner circumferential side piston to be assembled into the stereogram that outer circumferential side piston is installed to after the eccentric part of crank axle to the state before this inner circumferential side piston.

Fig. 6 is figure rotary compressor, that piston is installed to the method on eccentric part for embodiment of the present invention is described, is to represent inner circumferential side piston to be assembled into the figure that outer circumferential side piston has been installed to after the eccentric part of crank axle to the state of this inner circumferential side piston.

Fig. 7 is near the detail drawing of eccentric part that represents rotary compressor before.

Detailed description of the invention

Embodiment

Fig. 1 is the longitudinal section that represents the rotary compressor of embodiment of the present invention. Fig. 2 is the sectional elevation that represents the compression mechanical part of this rotary compressor. Fig. 3 is the key diagram of the inner circumferential side piston for this rotary compressor is described, is (a) longitudinal section that represents crank axle and inner circumferential side piston, (b) is the top view that represents inner circumferential side piston.

The structure of the rotary compressor of present embodiment is described with Fig. 1～Fig. 3 below.

Rotary compressor 100, is receiving the motor 2 being made up of stator 2a and rotor 2b and the compression mechanical part 3 being driven by motor 2 closed container 1 is interior. The revolving force of motor 2 is delivered to compression mechanical part 3 via crank axle 4. In addition, in closed container 1, storing the lubricating oil (refrigerator oil) of lubricious compression mechanical part 3.

Crank axle 4 has main shaft 4a on the rotor 2b that is fixed on motor 2, is located at the countershaft 4b of main shaft 4a opposition side and is formed on main shaft 4a the eccentric part 4c between countershaft 4b.

In addition, in the present embodiment, the shape of crank axle 4 forms as described below. , in the present embodiment, in order to increase the discharge capacity of rotary compressor 100, when increasing, the external diameter that suppresses eccentric part 4c increase the offset (with respect to the offset of main shaft 4a and countershaft 4b) of eccentric part 4c. For this reason, the outer peripheral face (outer peripheral face eccentric part 4c, eccentric direction opposition side) that crank axle 4 is formed as the anti-eccentric side of eccentric part 4c is than the recessed shape of peripheral part of main shaft 4a and countershaft 4b. In other words, when the offset (distance between the central shaft of the central shaft of main shaft 4a and countershaft 4b and eccentric part 4c) that is Re, eccentric part 4c at the radius of establishing eccentric part 4c is e, be Re-e from the central shaft of main shaft 4a and countershaft 4b to the distance the outer peripheral face of the anti-eccentric side of eccentric part 4c. Therefore,, when the radius that is Rm, countershaft 4b at the radius of establishing main shaft 4a is Ra, the crank axle 4 of rotary compressor 100 becomes Re-e < Rm, Re-e < Ra.

The crank axle 4 forming like this rotates supporting freely by base bearing 5 and supplementary bearing 6. Specifically, base bearing 5 is located at the top of compression mechanical part 3, by the main shaft 4a rotation supporting freely of crank axle 4. In addition, supplementary bearing 6 is located at the bottom of compression mechanical part 3, by the countershaft 4b rotation supporting freely of crank axle 4.

Compression mechanical part 3 has cylinder 7, piston 20 and blade 9 etc.

Cylinder 7 is fixed on the interior perimembranous of closed container 1, and heart portion has cylinder chamber cylindraceous therein. In this cylinder chamber, be provided with piston 20, this piston 20 is embedded in the eccentric part 4c of crank axle 4 sliding freely. In addition, the direction of principal axis both ends of the surface of the cylinder chamber of cylinder 7 are by base bearing 5 and 6 obturations of supplementary bearing. Be provided with the reciprocating blade 9 along with the rotation of eccentric part 4c at cylinder 7. , become discharge chambe by the outer peripheral face of piston 20, the inner peripheral surface of cylinder chamber and the space that blade 9 is divided. In addition, in this discharge chambe, (in cylinder chamber) is divided into space, high-pressure side and low-pressure side space by blade 9.

At this, in the present embodiment, piston 20 forms as shown in Figures 2 and 3.

, piston 20 is made up of inner circumferential side piston 21 and outer circumferential side piston 22. Inner circumferential side piston 21 is arranged at the outer peripheral face of eccentric part 4c sliding freely. Outer circumferential side piston 22 is for example arranged at the outer peripheral face of this inner circumferential side piston 21 sliding freely. Inner circumferential side piston 21 is made up of multiple arc-shaped part 21a, and the plurality of arc-shaped part 21a is split to form at the section of the central shaft along eccentric part 4c. In the present embodiment, inner circumferential side piston 21 is made up of 2 arc-shaped part 21a.

In the rotary compressor 100 forming like this, by rotor, 2b rotates, and the crank axle 4 being embedded in rotor 2b rotates. Like this, be installed on sliding freely the piston 20 of the eccentric part 4c of crank axle 4, in the cylinder chamber of cylinder 7, carry out eccentric rotary motion. Along with the eccentric rotary motion of piston 20, the volume in the space, high-pressure side of cylinder 7 reduces gradually, and the refrigerant gas in space, high-pressure side is compressed. Refrigerant gas after this is compressed be discharged to closed container 1 interior after, deliver to outside from discharge pipe 11. In addition, be adjacent to be provided with reservoir 12 with closed container 1, this reservoir 12 is communicated with the cylinder chamber of cylinder 7 via suction connection 10. ,, via reservoir 12 and suction connection 10, refrigerant gas is sent to the cylinder chamber of cylinder 7.

With Fig. 4～Fig. 6, the method that piston 20 is installed to the eccentric part 4c of crank axle 4 is described below.

Fig. 4 is figure rotary compressor, that piston is installed to the method on eccentric part for embodiment of the present invention is described, is the eccentric part stereogram of state before that represents inner circumferential side piston to be assembled into crank axle. Fig. 5 for this rotary compressor is described, piston is installed to the figure of the method for eccentric part, be to represent inner circumferential side piston to be assembled into the stereogram that outer circumferential side piston is arranged on after the eccentric part of crank axle to state before this inner circumferential side piston. Fig. 6 for this rotary compressor is described, piston is installed to the figure of the method for eccentric part, be to represent inner circumferential side piston to be assembled into the figure that outer circumferential side piston is arranged on after the eccentric part of crank axle to the state of this inner circumferential side piston. Specifically, Fig. 6 (a) is the longitudinal section that represents outer circumferential side piston to be assembled in the state of inner circumferential side piston. Fig. 6 (b) is the stereogram that represents outer circumferential side piston to be assembled in the state of inner circumferential side piston. Fig. 6 (c) is the top view that represents outer circumferential side piston to be assembled in state on the piston of inner circumferential side. In Fig. 6 (c), omit the diagram of crank axle.

On the eccentric part 4c that piston 20 will be installed to crank axle 4 time, as shown in Figure 4, first inner circumferential side piston 21 is arranged on eccentric part 4c. Specifically, to sandwich the mode of eccentric part 4c with 2 arc-shaped part 21a that form inner circumferential side piston 21, be inner circumferential side piston 21 by 2 arc-shaped part 21a() be installed on eccentric part 4c. In other words,, 2 arc-shaped part 21a that form inner circumferential side piston 21, from the direction vertical with the central shaft of eccentric part 4c, be arranged on eccentric part 4c.

As mentioned above, the inner circumferential side piston of rotary compressor is before formed by overall thing. Therefore, rotary compressor before, for inner circumferential side piston being installed on the eccentric part of crank axle, the outer peripheral face of the anti-eccentric side that the pattern of wants is eccentric part is more outstanding than the outer peripheral face of main shaft or countershaft. Or, the outer peripheral face of the outer peripheral face of the anti-eccentric side of eccentric part and main shaft or countershaft need to be formed as to the same face. In other words, rotary compressor before can not be arranged on inner circumferential side piston the crank axle of the outer peripheral face of anti-eccentric side of the crank axle 4(eccentric part 4c of this shape of the present embodiment shape more recessed than the peripheral part of main shaft 4a and countershaft 4b) on. But, by forming inner circumferential side piston 21 with 2 arc-shaped part 21a as in the present embodiment, even for the crank axle 4 of the outer peripheral face of the anti-eccentric side of the eccentric part 4c shape more recessed than the outer peripheral face of main shaft 4a or countershaft 4b, inner circumferential side piston 21 also can be installed.

As shown in Figure 4, inner circumferential side piston 21 be installed to the eccentric part 4c of crank axle 4 upper after, as shown in Figure 5 and Figure 6, outer circumferential side piston 22 is arranged on to the outer peripheral face of this inner circumferential side piston 21. Specifically, main shaft 4a or countershaft 4b are passed to the outer circumferential side piston 22 of the integration that is formed as general cylindrical shape. Then, this outer circumferential side piston 22 is arranged on to the outer peripheral face of inner circumferential side piston 21.

In addition, in the present embodiment, as shown in Figure 3, in the time that the radius of establishing inner circumferential side piston 21 is Rp, Rp-e is the value larger than the radius R m of main shaft 4a. Therefore, be arranged under the state on eccentric part 4c at inner circumferential side piston 21, the outer peripheral face of the anti-eccentric side of inner circumferential side piston 21 is more outstanding than the outer peripheral face of main shaft 4a. Like this, outer circumferential side piston 22 can be installed to eccentric part 4c from main shaft 4a side. In addition, in the present embodiment, as shown in Figure 3, in the time that the radius of establishing inner circumferential side piston 21 is Rp, Rp-e is the value larger than the radius R a of countershaft 4b. Therefore, be arranged under the state on eccentric part 4c at inner circumferential side piston 21, the outer peripheral face of the anti-eccentric side of inner circumferential side piston 21 is more outstanding than the outer peripheral face of countershaft 4b. Therefore, outer circumferential side piston 22 can also be installed to eccentric part 4c from countershaft 4b side.

As mentioned above, the rotary compressor 100 forming as in the present embodiment can obtain following effect.

, as mentioned above, the inner circumferential side piston of rotary compressor is before made up of overall thing. Therefore, rotary compressor before, for inner circumferential side piston being installed on the eccentric part of crank axle, the outer peripheral face of the anti-eccentric side that the pattern of wants is eccentric part is more outstanding than the outer peripheral face of main shaft or countershaft. Or, the outer peripheral face of the outer peripheral face of the anti-eccentric side of eccentric part and main shaft or countershaft need to be formed as to the same face. Therefore, this structure of rotary compressor has before restricted the expansion of discharge capacity. But the rotary compressor of present embodiment is this restriction not, even for the crank axle 4 of the outer peripheral face of the anti-eccentric side of the eccentric part 4c shape more recessed than the peripheral part of main shaft 4a and countershaft 4b, inner circumferential side piston 21 also can be installed. Therefore, the rotary compressor of present embodiment, is not subject to above-mentioned restriction, can expand discharge capacity (, can realize high output).

At this, about the method for discharge capacity that expands rotary compressor, also considered the offset of eccentric part and piston to remain unchanged and the method for increasing the height of piston and cylinder. But, between the outer peripheral face (outer peripheral face of the eccentric direction side of eccentric part) and cylinder chamber's inner peripheral surface of the eccentric side of piston, be in cylinder chamber, to be separated into the sealing of low-voltage space and high-pressure space. Therefore,, if increase the height of piston and cylinder, the length of sealing portion increases. Therefore, while realizing the ability increase of rotary compressor with the height of increasing piston and cylinder, the refrigerant gas of high-pressure space side can leak to low-voltage space side, the weight flow that sucks the refrigerant gas of (in cylinder chamber) in discharge chambe reduces, thereby can cause the efficiency of rotary compressor significantly to reduce. But the rotary compressor 100 of present embodiment, as mentioned above, does not increase the height of piston 20 and cylinder 7, just can expand discharge capacity. , the rotary compressor 100 of present embodiment can not cause the remarkable reduction of the efficiency being produced by the refrigrant leakage at the sealing place between piston 20 and cylinder chamber's inner peripheral surface, can expand discharge capacity.

In other words, improving the efficiency of rotary compressor in order not change discharge capacity, reduce the height of piston 20 and cylinder 7, the refrigerant gas amount that minimizing is leaked from high-pressure space side direction low-voltage space side at the sealing place being formed between the two, is very important. At this moment, reduce the height of piston and cylinder in order not change discharge capacity, must increase the offset of the eccentric part of crank axle. But rotary compressor before, due to above-mentioned restriction, can not too increase the offset of eccentric part. Therefore, the amplitude of the improved efficiency of rotary compressor is before very little. And the rotary compressor 100 of present embodiment, owing to there is no above-mentioned restriction, so, compared with before, can increase significantly the offset of eccentric part 4c. Therefore, the rotary compressor 100 of present embodiment can be than greatly improving before efficiency.

In addition, improve the efficiency of rotary compressor in order not change discharge capacity, in order to reduce the sliding speed of outer peripheral face and piston inner peripheral surface of eccentric part, the radius (in other words diameter) that reduces eccentric part is also very important. But rotary compressor before, due to above-mentioned restriction, in the time will increasing the offset of eccentric part, can not too reduce the radius of eccentric part. This is because if reduced the radius of eccentric part, can cause the outer peripheral face of anti-eccentric side of eccentric part more recessed than the outer peripheral face of main shaft or countershaft. Therefore, rotary compressor before, the improvement amplitude of improving efficiency with the radius that reduces eccentric part is very little. And the rotary compressor 100 of present embodiment, owing to there is no above-mentioned restriction, so, making the offset of eccentric part 4c when identical before, can be than the radius that reduces before eccentric part 4c. Therefore, the rotary compressor 100 of present embodiment can further improve efficiency.

In addition, in the present embodiment, the example that inner circumferential side piston 21 is divided into 2 arc-shaped part 21a is described, still, inner circumferential side piston 21 can certainly be divided into 3 above arc-shaped part 21a. Form the number of the arc-shaped part 21a of inner circumferential side piston 21 by increase, the size of material therefor can reduce to manufacture inner circumferential side piston 21 time, so, can improve the yield rate of material, the efficiency of loading while also improving transport of materials. That is, form the number of the arc-shaped part 21a of inner circumferential side piston 21 by increase, can play the effect that cheap for manufacturing cost and high efficiency rotary compressor 100 can be provided.

In addition, in the present embodiment, the rotary compressor 100 with 1 compression mechanical part 3 has been described, still, rotary compressor 100 also can be configured to the multi-cylinder rotary air compressor with multiple compression mechanical parts 3. At this moment, formed multiple eccentric part 4c between main shaft 4a and countershaft 4b, these eccentric parts 4c is connected by jackshaft. In addition, be provided with accordingly multiple cylinders 7 with each eccentric part 4c, the demarcation strip institute that is arranged on 7, cylinder at the end face of the cylinder chamber of 7 openings of each cylinder is inaccessible. In addition, in the time that rotary compressor 100 is configured to multi-cylinder rotary air compressor, preferably each eccentric part 4c with respect to the central shaft of main shaft 4a and countershaft 4b axisymmetric configure. For example, when rotary compressor 100 is double cylinder rotary compressor, preferably 2 eccentric part 4c are formed as to the phase difference of 180 ° with respect to the central shaft of main shaft 4a and countershaft 4b. By the each eccentric part 4c of such formation, can suppress vibration causing because of the rotation of crank axle 4 etc.

In addition, in the present embodiment, do not address especially the relation in " gap between the inner peripheral surface of the outer peripheral face of eccentric part 4c and inner circumferential side piston 21 " and " gap between the inner peripheral surface of the outer peripheral face of inner circumferential side piston 21 and outer circumferential side piston 22 ", but, two gaps can be for example roughly the same size (below, " roughly the same ", basic identical, be called " identical ". , " identical " described in present embodiment is not proper identical). For example, if the size in " gap between the inner peripheral surface of the outer peripheral face of eccentric part 4c and inner circumferential side piston 21 " and " gap between the inner peripheral surface of the outer peripheral face of inner circumferential side piston 21 and outer circumferential side piston 22 " differs too large, the poor of " frictional force between the inner peripheral surface of the outer peripheral face of eccentric part 4c and inner circumferential side piston 21 " and " frictional force between the inner peripheral surface of the outer peripheral face of inner circumferential side piston 21 and outer circumferential side piston 22 " increases. Therefore, the rotary speed of inner circumferential side piston 21 and outer circumferential side piston 22 is significantly different, and the sliding speed of the inner peripheral surface of the outer peripheral face of inner circumferential side piston 21 and outer circumferential side piston 22 accelerates, and may cause the inordinate wear of this part. But, by the size in " gap between the inner peripheral surface of the outer peripheral face of eccentric part 4c and inner circumferential side piston 21 " and " gap between the inner peripheral surface of the outer peripheral face of inner circumferential side piston 21 and outer circumferential side piston 22 " is become identical, the sliding speed that can keep rightly the outer peripheral face of inner circumferential side piston 21 and the inner peripheral surface of outer circumferential side piston 22, can prevent the inordinate wear of this part.

In addition, in the rotary compressor 100 of present embodiment, inner circumferential side piston 21 is partition members, and outer circumferential side piston 22 is monolithic molding parts, so, can form by different separately materials. At this moment, preferably select two materials, so that the material of the material of inner circumferential side piston 21 and outer circumferential side piston 22 is identical linear expansion coefficient. When rotary compressor 100 turns round, inner circumferential side piston 21 and outer circumferential side piston 22 produce thermal expansion. At this moment,, if both difference of linear expansions are excessive, the poor of " gap between inner circumferential side piston 21 and base bearing 5 and supplementary bearing 6 " and " gap between outer circumferential side piston 22 and base bearing 5 and supplementary bearing 6 " increases. Therefore, the poor of " frictional force between inner circumferential side piston 21 and base bearing 5 and supplementary bearing 6 " and " frictional force between outer circumferential side piston 22 and base bearing 5 and supplementary bearing 6 " increases. Therefore, the rotary speed of inner circumferential side piston 21 and outer circumferential side piston 22 is significantly different, and the sliding speed of the inner peripheral surface of the outer peripheral face of inner circumferential side piston 21 and outer circumferential side piston 22 accelerates, and may cause the inordinate wear of this part. But, so that the material of the material of inner circumferential side piston 21 and outer circumferential side piston 22 is identical linear expansion coefficients, can make " gap between inner circumferential side piston 21 and base bearing 5 and supplementary bearing 6 " identical with " gap between outer circumferential side piston 22 and base bearing 5 and supplementary bearing 6 " by selecting two materials. Therefore, the sliding speed of the outer peripheral face of inner circumferential side piston 21 and the inner peripheral surface of outer circumferential side piston 22 can be kept rightly, the inordinate wear of this part can be prevented.

The explanation of Reference numeral

1 ... closed container, 2 ... motor, 2a ... stator, 2b ... rotor, 3 ... compression mechanical part, 4 ... crank axle, 4a ... main shaft, 4b ... countershaft, 4c ... eccentric part, 5 ... base bearing, 6 ... supplementary bearing, 7 ... cylinder, 9 ... blade, 10 ... suction connection, 11 ... discharge pipe, 12 ... reservoir, 20 ... piston, 21 ... inner circumferential side piston, 21a ... arc-shaped part, 22 ... outer circumferential side piston, 50 ... inner circumferential side piston (before), 100 ... rotary compressor.

Claims

1. a rotary compressor, has:

Motor, this motor has stator and rotor;

Crank axle, this crank axle, by above-mentioned Motor Drive, has the master of being fixed on above-mentioned rotorAxle, be located at above-mentioned main shaft axial opposition side countershaft and be formed on above-mentioned main shaft withEccentric part between above-mentioned countershaft;

Compression mechanical part, this compression mechanical part has and is installed on sliding freely above-mentioned eccentric partPiston, be formed with cylinder chamber cylindraceous and in this cylinder chamber, configuring above-mentioned eccentric part and onState the cylinder of piston and will in above-mentioned cylinder chamber, be separated into the leaf of low-voltage space and high-pressure spaceSheet; And

Closed container, this closed container is accommodated above-mentioned motor, above-mentioned crank axle and above-mentioned compressionPortion of mechanism; Above-mentioned rotary compressor is characterised in that,

Above-mentioned piston by be located at sliding freely above-mentioned eccentric part outer peripheral face inner circumferential side piston andThe outer circumferential side piston that is located at the outer peripheral face of this inner circumferential side piston forms;

Above-mentioned inner circumferential side piston is made up of multiple arc-shaped parts,

The radius that is Rm, above-mentioned countershaft at the radius of establishing above-mentioned main shaft is Ra, above-mentioned eccentric partRadius be that the radius of Re, above-mentioned inner circumferential side piston is the offset of Rp and above-mentioned eccentric partDuring for e, there is the relation of Re-e < Rm < Rp-e and Re-e < Ra < Rp-e.

2. rotary compressor as claimed in claim 1, is characterized in that, lives in above-mentioned inner circumferential sidePlug is made up of 3 above above-mentioned arc-shaped parts.

3. rotary compressor as claimed in claim 1 or 2, is characterized in that, above-mentioned crankThe above-mentioned eccentric part of axle and above-mentioned compressor structure portion are provided with multiple.

4. rotary compressor as claimed in claim 1, is characterized in that, is formed on above-mentioned inclined to one sideGap between the inner peripheral surface of the outer peripheral face of heart portion and above-mentioned inner circumferential side piston and being formed onStating the gap between outer peripheral face and the above-mentioned outer circumferential side piston of inner circumferential side piston, is identical.

5. rotary compressor as claimed in claim 1, is characterized in that, above-mentioned outer circumferential side is livedThe linear expansion coefficient of plug and the linear expansion coefficient of above-mentioned inner circumferential side piston are identical.