CN101871443A - Hermetic type compressor and refrigeration plant - Google Patents
Hermetic type compressor and refrigeration plant Download PDFInfo
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- CN101871443A CN101871443A CN 201010167333 CN201010167333A CN101871443A CN 101871443 A CN101871443 A CN 101871443A CN 201010167333 CN201010167333 CN 201010167333 CN 201010167333 A CN201010167333 A CN 201010167333A CN 101871443 A CN101871443 A CN 101871443A
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 13
- 239000003921 oil Substances 0.000 claims abstract description 245
- 239000000446 fuel Substances 0.000 claims abstract description 186
- 239000000314 lubricant Substances 0.000 claims abstract description 129
- 230000002093 peripheral effect Effects 0.000 claims abstract description 17
- 239000010687 lubricating oil Substances 0.000 claims abstract description 8
- 238000003825 pressing Methods 0.000 claims description 19
- 230000005489 elastic deformation Effects 0.000 claims description 7
- 230000008093 supporting effect Effects 0.000 description 9
- 238000001816 cooling Methods 0.000 description 7
- 238000005461 lubrication Methods 0.000 description 7
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 239000004215 Carbon black (E152) Substances 0.000 description 3
- CBENFWSGALASAD-UHFFFAOYSA-N Ozone Chemical compound [O-][O+]=O CBENFWSGALASAD-UHFFFAOYSA-N 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 3
- 238000009825 accumulation Methods 0.000 description 3
- 238000009826 distribution Methods 0.000 description 3
- 229930195733 hydrocarbon Natural products 0.000 description 3
- 150000002430 hydrocarbons Chemical class 0.000 description 3
- 229920001707 polybutylene terephthalate Polymers 0.000 description 3
- 239000000843 powder Substances 0.000 description 3
- 238000005096 rolling process Methods 0.000 description 3
- 239000007921 spray Substances 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000005520 cutting process Methods 0.000 description 2
- 230000003584 silencer Effects 0.000 description 2
- -1 Polybutylene terephthalate Polymers 0.000 description 1
- 230000003321 amplification Effects 0.000 description 1
- BGOFCVIGEYGEOF-UJPOAAIJSA-N helicin Chemical compound O[C@@H]1[C@@H](O)[C@H](O)[C@@H](CO)O[C@H]1OC1=CC=CC=C1C=O BGOFCVIGEYGEOF-UJPOAAIJSA-N 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000009740 moulding (composite fabrication) Methods 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
- 210000000707 wrist Anatomy 0.000 description 1
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Abstract
The invention provides a kind of hermetic type compressor and refrigeration plant.Accumulating in seal container has lubricant oil, and electric element and compressing member have been taken in, compressing member comprises axle, cylinder block, piston, linking department, main bearing, a plurality of ball and thrust ball bearing, axle has from the peripheral part of the axle fuel feeding portion to interior all supplying lubricating oils of thrust ball bearing, interior perimembranous in holding part is equipped with the bearing extension part that the main bearing extension forms, and be provided with the axle direction gap between the upper end of bearing extension part and top race, the axle direction gap forms the stream of lubricant oil.
Description
Technical field
The present invention relates to a kind of hermetic type compressor and refrigeration plant.
Background technique
In recent years, the hermetic type compressor that uses in refrigeration plants such as freezing-cooling storeroom can reduce the high efficiency, low noiseization and the high reliabilityization that consume electric power and desirable with it always.
At present, this hermetic type compressor adopts thrust ball bearing to raise the efficiency.
Below, with reference to accompanying drawing above-mentioned existing hermetic type compressor is described.
The longitudinal section of the existing hermetic type compressor that Figure 17 is put down in writing for Japanese Unexamined Patent Application Publication 2005-500476 communique, Figure 18 are the enlarged view of critical piece of the thrust ball bearing of existing hermetic type compressor.
In Figure 17 and Figure 18, accumulating in the bottom of seal container 2 has lubricant oil 4.Compressor main body 6 is flexibly supported with respect to seal container 2 by suspended spring 8.
Compressor main body 6 is made of electric element 10 and the compressing member 12 that is equipped on electric element 10 tops.Electric element 10 is made of stator 14 and rotor 16.
The axle 18 of compressing member 12 comprises main shaft part 20 and eccentric axial portion 22.Main shaft part 20 can be rotated the main bearing 26 that freely is supported on cylinder block (cylinder block) 24 by axle, and is fixed with rotor 16.And, axle 18 constitute eccentric axial portion 22 with respect to the load effect only be disposed at eccentric axial portion 22 downside main shaft part 20 and by the cantilever bearings of main bearing 26 supportings.
In addition, axle 18 has the oil feeding mechanism 28 that is made of the spiral helicine groove that is arranged at main shaft part 20 surfaces etc.And then axle 18 has the fuel supply path 29 that is communicated with and extends to the top of eccentric axial portion 22 with the upper end of oil feeding mechanism 28.
Piston 30 can be inserted in the cylinder 34 of the internal surface with the general cylindrical shape that is formed at cylinder block 24 in reciprocal mode freely.In addition, linking department 36 is intercalated in wrist pin 38 respectively by the hole portion (not shown) that will be arranged on two ends and eccentric axial portion 22 links eccentric axial portion 22 and piston 30.
Then, the thrust ball bearing 76 that is arranged at main bearing 26 is described.
As shown in figure 18, main bearing 26 comprises that thrust face 60 and specific thrust face 60 as the planar surface portion vertical with the axle center further prolongs, has the bearing extension part 62 with main shaft part 20 interior surface opposing upward.
In addition, dispose the thrust ball bearing 76 that constitutes by top race (race) 64, the ball 66, bottom race 70 and the support unit 72 that keep by holding part (holder) 68 in external diameter one side of bearing extension part 62.
In addition, on thrust face 60, support unit 72, bottom race 70, ball 66, top race 64 be the state stack to join mutually successively.Axle 18 lip part 74 falls within the upper surface of top race 64, is provided with the axle direction gap 78 of regulation between the upper end of bearing extension part 62 and lip part 74.
Below, the action of the hermetic type compressor of formation is as previously discussed described.
When to electric element 10 energisings, the rotating magnetic field that produces at stator 14 is rotated rotor 16 and main shaft part 20 in the lump.By the rotation of main shaft part 20, eccentric axial portion 22 is carried out eccentric motion, and the eccentric motion of eccentric axial portion 22 is delivered to piston 30 via linking department 36, piston 30 to-and-fro motion in cylinder 34.
Refrigeration cycle (not shown) outside the seal container 2 and cold medium that returns is imported in the pressing chamber 48 via absorbing silencer 52 utilizes piston 30 to compress in pressing chamber 48, and the cold medium after the compression is sent to refrigeration cycle from seal container 2.
In addition, the lower end of axle 18 impregnated in the lubricant oil 4.By the rotation of axle 18, lubricant oil 4 utilizes 28 pairs of main shaft part 20 of oil feeding mechanism to be lubricated, and then, it is fed to thrust ball bearing 76 from axle direction gap 78.And then lubricant oil 4 is fed to the each several part of compressing member 12 via fuel supply path 29, and slide part is lubricated.
Summary of the invention
Yet, in the structure of above-mentioned existing hermetic type compressor, be difficult to lubricant oil 4 be distributed and feeds to the each several part of thrust ball bearing 76 and compressing member 12 according to the ratio of expectation.In order to distribute according to the ratio of expectation, can consider to make axle direction gap 78 to narrow down, still, in this case, the upper end of bearing extension part 62 will contact with the lip part 74 of axle 18.Therefore, existing hermetic type compressor exists that noise is big, efficient is low and the problem of poor reliability.
The present invention finishes in order to solve above-mentioned existing problem, and its purpose is to provide a kind of can guarantee axle direction gap and the hermetic type compressor that noise is little, efficient is high, reliability is high.
Therefore, hermetic type compressor of the present invention constitutes: accumulating in seal container has lubricant oil, and the compressing member of taking in the electric element that possesses stator and rotor and driving by described electric element, compressing member comprises: have the main shaft part of extending on vertical direction and the axle of eccentric axial portion; Form the cylinder block of columnar pressing chamber; Can be inserted in the piston of pressing chamber inside in reciprocating mode; The linking department that links piston and eccentric axial portion; Be arranged at cylinder block, form the main bearing of cantilever bearings by axle supporting spindle portion; And thrust ball bearing, this thrust ball bearing has the thrust face that is equipped on main bearing and is held in a plurality of balls of holding part and is equipped on the top race and the bottom race of the upper and lower sides of ball respectively, axle has from the peripheral part of the axle fuel feeding portion to interior all supplying lubricating oils of thrust ball bearing, interior perimembranous in holding part is equipped with the bearing extension part that the main bearing extension forms, and be provided with the axle direction gap between the upper end of bearing extension part and top race, the axle direction gap forms the stream of lubricant oil.
Such hermetic type compressor is by guaranteeing the axle direction gap, only utilizes thrust ball bearing to come load on the vertical direction such as deadweight of supporting axle and rotor.Thereby, a kind of hermetic type compressor can be provided, it can prevent that the upper end of bearing extension part from contacting with top race, and thrust ball bearing is carried out sufficient fuel feeding, and noise is low, efficient is high, reliability is high.
Description of drawings
Fig. 1 is the longitudinal section of the hermetic type compressor of embodiment of the present invention 1;
Fig. 2 is the sectional view of the critical piece on the axle side surface direction of hermetic type compressor of this mode of execution 1;
Fig. 3 is the sectional view of the critical piece of axle on the frontal of the hermetic type compressor of this mode of execution 1;
Fig. 4 is the sectional view of the critical piece on the axle side surface direction of hermetic type compressor of this mode of execution 1;
Fig. 5 is the stereogram of main bearing of the hermetic type compressor of this mode of execution 1;
Fig. 6 is the longitudinal section of the hermetic type compressor of embodiment of the present invention 2;
Fig. 7 is the sectional view of the critical piece on the axle side surface direction of hermetic type compressor of this mode of execution 2;
Fig. 8 is the sectional view of the critical piece of axle on the frontal of the hermetic type compressor of this mode of execution 2;
Fig. 9 is the sectional view of the critical piece on the axle side surface direction of hermetic type compressor of this mode of execution 2;
Figure 10 is the stereogram of main bearing of the hermetic type compressor of this mode of execution 2;
Figure 11 is the longitudinal section of the hermetic type compressor of embodiment of the present invention 3;
Figure 12 is the sectional view of the critical piece on the axle side surface direction of hermetic type compressor of this mode of execution 3;
Figure 13 is the sectional view of the critical piece of axle on the frontal of the hermetic type compressor of this mode of execution 3;
Figure 14 is the sectional view of critical piece of axle side surface direction of the hermetic type compressor of this mode of execution 3;
Figure 15 is the stereogram of main bearing of the hermetic type compressor of this mode of execution 3;
Figure 16 is the refrigeration plant of this mode of execution 3;
Figure 17 is the longitudinal section of existing hermetic type compressor;
Figure 18 is the enlarged view of critical piece of the thrust ball bearing of this hermetic type compressor.
Embodiment
Below, with reference to accompanying drawing embodiments of the present invention are described.
(mode of execution 1)
Fig. 1 is the longitudinal section of the hermetic type compressor of embodiment of the present invention 1, Fig. 2 is the sectional view of the critical piece on the axle side surface direction of this hermetic type compressor, Fig. 3 is the sectional view of the critical piece of axle on the frontal of this hermetic type compressor, Fig. 4 is the sectional view of the critical piece on the axle side surface direction of this hermetic type compressor, and Fig. 5 is the stereogram of the main bearing of this hermetic type compressor.That is, the axle 110 among Fig. 2 obtains the critical piece amplification of Fig. 4.
In Fig. 1～Fig. 5, accumulating in seal container 101 has lubricant oil 102, and takes in electric element 105 that is made of stator 103 and rotor 104 and the compressing member 106 that is driven by electric element 105.Compressing member 106 comprises axle 110, cylinder block 114, piston 126, linking department 128, main bearing 120 and thrust ball bearing 132.
The eccentric axial portion 112 that axle 110 has the main shaft part 111 that is fixed with rotor 104 and the top that is equipped on main shaft part 111 and forms prejudicially with respect to main shaft part 111.Here, main shaft part 111 and eccentric axial portion 112 are extended on vertical direction.
The main bearing 120 of cylinder block 114 comprises: with the axle center of main bearing 120 generally perpendicularly, the thrust face 130 that forms in the form of a ring; With further prolong upward from thrust face 130 and have a bearing extension part 144 with main shaft part 111 interior surface opposing.That is, bearing extension part 144 extends to the interior perimembranous of the holding part 133 that constitutes thrust ball bearing 132 described later.In addition, main bearing 120 has the discharge path 168 that is communicated with below vertical direction in the outside of bearing extension part 144.
In addition, at vertical direction upper support axle 110, dispose support unit 162, bottom race 136, a plurality of ball 134 successively and keep the holding part 133 and the top race 135 of ball 134 to upside from the thrust face 130 in the outside of bearing extension part 144.Therefore, top race 135 and bottom race 136 are equipped on the upper and lower sides of ball 134 respectively.
Constitute thrust ball bearing 132 by this bottom race 136, a plurality of ball 134 and holding part 133 and top race 135.
And then support unit 162, bottom race 136, a plurality of ball 134 and holding part 133 all are disposed at the outside of bearing extension part 144 in the mode of guaranteeing the radial direction gap.
On the other hand, top race 135 is equipped on the position of more leaning on upside than the upper end 170 of bearing extension part 144.The distance of 134 the topmost part (highly) is longer than the distance (highly) of the upper end 170 from thrust face 130 to bearing extension part 144 from thrust face 130 to ball, utilize its difference in size, between the upper end of bearing extension part 144 and top race 135, be formed with the axle direction gap 146 of regulation.Axle direction gap 146 forms the stream of lubricant oil 102.
Here, support unit 162 as the bigger wave washer of rigidity or the elastic member of hard etc. on vertical direction, possess elasticity, can resiliently deformable parts.And the elastic deformation amount of support unit 162 on vertical direction is set at bigger than axle direction gap 146.
Then, the detailed structure to the fuel supply path of axle 110 describes.
Here, first fuel supply path 150 is made of concentric pump 150a, cross-drilled hole 150b, spiral oil supply 150c.Pump 150a is arranged at the bottom of axle 110 with one heart.Cross-drilled hole 150b is communicated with, extends on radial direction with the top of concentric pump 150a.Spiral oil supply 150c, its lower end is communicated with cross-drilled hole 150b at the peripheral part of axle 110, and the upper end is communicated with the groove 154 of the slit-shaped of second fuel supply path 152.
In addition, main shaft part 111 also comprises cross-drilled hole 158 and the 3rd fuel supply path 160.Here, the radial direction along main shaft part 111 extends cross-drilled hole 158 from the upper end of spiral oil supply 150c.The 3rd fuel supply path 160, its lower end is communicated with the bottom of cross-drilled hole 158 is neighbouring, extends to the top of eccentric axial portion 112.That is, an end of the 3rd fuel supply path 160 is communicated with first fuel supply path 150.
In order to improve based on the rotation of axle 110 and the conveying capacity of the lubricant oil 102 that produces, the 3rd fuel supply path 160 extends upward along with it and tilts in the mode away from the axle center of main shaft part 111, and the topmost part is at the upper end of eccentric axial portion 112 112a opening.
In addition, in embodiments of the present invention 1, hermetic type compressor 100 employed cold media are to serve as that zero R134a, R600a are that the lower cold naturally medium of warmization coefficient of representative is the cold medium of hydrocarbon class etc. with the ozone layer destroying coefficient, higher with compatibility respectively lubricant oil 102 combinations.
Below, the action of the hermetic type compressor 100 that constitutes is like that as previously discussed described.
The rotor 104 of electric element 105 makes axle 110 rotations, and rotatablely moving of eccentric axial portion 112 is delivered to piston 126 by linking department 128, makes piston 126 to-and-fro motion in pressing chamber 116.Thus, cold medium is inhaled in the pressing chamber 116 from cooling system (not shown), sprays to cooling system after the compression again.
The weight of axle 110 and rotor 104 is by thrust ball bearing 132 supportings.In addition, when axle 110 rotations, owing to ball 134 rolls between top race 135 and bottom race 136, thereby smooth rotation.
By using thrust ball bearing 132, make the torque ratio of axle 110 rotations not use the thrust slide bearing of ball little.Therefore, the hermetic type compressor of embodiment of the present invention 1 can reduce the loss at thrust-bearing, thereby can reduce input, realization high efficiency.
Then, utilize because the centrifugal force that the rotation of axle 110 produces, by as first fuel supply path 150 that is arranged at a fuel feeding portion 140 of spools 110, the lubricant oil 102 that will accumulate in seal container 101 is drawn onto top from the bottom of main shaft 111.
Oil stream (the representing) 161 that will be distributed into oil stream (the representing) 151 that flows to second fuel supply path 152 by the lubricant oil 102 that first fuel supply path 150 is transported to the top of main shaft part 111 and flow to the 3rd fuel supply path 160 with arrow with arrow.Here, the oil stream 151 that flows to second fuel supply path 152 is the lubricant oil 102 of the groove 154 by slit-shaped is fed to the lubricant oil 102 of thrust ball bearing 132 via circumferential groove 152a oil stream.The oil stream 161 that flows to the 3rd fuel supply path 160 is that the oil of the lubricant oil 102 of lubricant oil 102 top that fed to eccentric axial portion 112 via cross-drilled hole 158 flows.
Owing between the upper end of bearing extension part 144 and top race 135, be formed with the axle direction gap 146 of regulation, therefore the oil stream 151 that flows to second fuel supply path 152 flows on radial direction via axle direction gap 146, forms the oil stream towards thrust ball bearing 132.
Particularly, the oil stream 151 that flows to second fuel supply path 152 forms the oil stream at the rolling position that directly flows to ball 134 and top race 135, thereby is reduced in the loss of ball 134 and top race 135 effectively.In addition, the oil stream 151 that flows to second fuel supply path 152 can reduce heat release, prevent to produce owing to what lack of lubrication caused and peel off equivalent damage.
And then, by changing the size in axle direction gap 146, can change the stream impedance of the oil stream 151 that flows to second fuel supply path 152.In addition, flow to the stream impedance of the oil stream 151 of second fuel supply path 152 by increase, lubricant oil 102 flows of the oil stream 161 that flows to the 3rd fuel supply path 160 are increased, perhaps on the contrary, the stream impedance of the oil stream 151 by reducing to flow to second fuel supply path 152 can make lubricant oil 102 flows of the oil stream 161 that flows to the 3rd fuel supply path 160 reduce.
Therefore, the lubricant oil 102 that is transferred to the top of main shaft part 111 by first fuel supply path 150 can be become to flow to the oil stream (flowing to the oil stream 151 of second fuel supply path 152) of the lubricant oil 102 of thrust ball bearing 132 with the pro rate of expectation and flow to the oil stream (flowing to the oil stream 161 of the 3rd fuel supply path 160) of lubricant oil 102 of the top of eccentric axial portion 112.In addition, the flow that is fed to the lubricant oil 102 of thrust ball bearing 132 can be adjusted into the best.
So, lubricant oil 102 is fed to thrust ball bearing 132 and eccentric axial portion 112 according to the oil mass of the best.Therefore, the hermetic type compressor of embodiment of the present invention 1 can reduce the slip loss, and can reduce heat release, prevents to produce owing to what lack of lubrication caused and peel off equivalent damage, thereby obtains higher reliability.
In addition, utilize the groove 154 of the slit-shaped of second fuel supply path 152 can carry out best distribution to above-mentioned lubricant oil 102 equally.
That is, the sectional area of the groove 154 by changing slit-shaped etc. even do not change axle direction gap 146, also can change the stream impedance of the oil stream 151 that flows to second fuel supply path 152.In addition, flow to the stream impedance of the oil stream 151 of second fuel supply path 152 by increase, lubricant oil 102 oil masses of the oil stream 161 that flows to the 3rd fuel supply path 160 are increased, perhaps on the contrary, the stream impedance of the oil stream 151 by reducing to flow to second fuel supply path 152 reduces lubricant oil 102 oil masses of the oil stream 161 that flows to the 3rd fuel supply path 160.Like this, by changing the stream impedance of second fuel supply path 152, also can adjust the flow of the lubricant oil 102 in interior week of being fed to thrust ball bearing 132.
In addition, the sectional area of groove 154 that also can be by changing axle direction gap 146 and slit-shaped is adjusted the flow of lubricant oil 102.Consequently, can distribute the oil stream (flowing to the oil stream 151 of second fuel supply path 152) of the lubricant oil 102 that flows to thrust ball bearing 132 and the oil stream (flowing to the oil stream 161 of the 3rd fuel supply path 160) of lubricant oil 102 that flows to the top of eccentric axial portion 112 according to the ratio of very refinement.
Then, in carrying during hermetic type compressor 100 etc., exist owing to the situation that impact load on the vertical direction that produces acts on electric element 105 and compressing member 106 such as falling.At this moment, the load on the vertical direction also acts on thrust ball bearing 132, and the support unit 162 that makes it possible to resiliently deformable produces resiliently deformable.That is, in support unit 162 can the deformation band of resiliently deformable, the axle direction gap 146 between the upper end of bearing extension part 144 and the top race 135 became zero, formed butt.This is because the elastic deformation amount of support unit 162 on vertical direction is set to bigger than axle direction gap 146.
Impact load on the vertical direction is done the time spent like this, is not thrust ball bearing 132 but upper end and top race 135 butts by bearing extension part 144 support this load, thereby can supports impact load.Therefore, the contact load that can prevent ball 134, top race 135 and bottom race 136 increases to extremely.
Consequently, the plastic deformation of thrust ball bearing 132 can be prevented, the slip of thrust ball bearing 132 can be maintained good state, so the hermetic type compressor of embodiment of the present invention 1 low noise, high efficiency and high reliability can be obtained.
Then, the oily stream to the lubricant oil 102 that fed to thrust ball bearing 132 illustrates.
After thrust ball bearing 132 was lubricated, the lubricant oil 102 that is fed to thrust ball bearing 132 can be accumulated in the outside of bearing extension part 144, made that thrust ball bearing 132 is soaked.Yet lubricant oil 102 can be via the discharge path 168 that is arranged at cylinder block 114, and the utilization deadweight is discharged to the space in the seal container 101.
Therefore, can always supply with new lubricant oil 102 circularly, and prevent that it from accumulating to thrust ball bearing 132.Consequently, the hermetic type compressor of embodiment of the present invention 1 can prevent the accumulation of abrasion powder etc., thereby can obtain higher reliability.
In addition, in present embodiment 1, the example that possesses second fuel supply path 152 is illustrated.Yet, also can only pass through axle direction gap 146, the oil stream (flowing to the oil stream 151 of second fuel supply path 152) of the lubricant oil 102 that flows to thrust ball bearing 132 and the oil stream (flowing to the oil stream 161 of the 3rd fuel supply path 160) of lubricant oil 102 that flows to the top of eccentric axial portion 112 be distributed according to the ratio of expectation.
In addition, as second fuel supply path 152, be illustrated extending along axle direction, but also can be the groove of other shapes, the fuel supply path of other modes in the groove 154 of the slit-shaped of the peripheral part of main shaft part 111.
In addition, in embodiments of the present invention 1, the example that discharge path 168 is arranged at cylinder block 114 is illustrated.But,, then also can be other structure if can after thrust ball bearing 132 is lubricated, be discharged to the space in the seal container 101 according to the mode that always new lubricant oil 102 can be fed to circularly thrust ball bearing 132.
In addition, in embodiments of the present invention 1, to the example that lubricant oil 102 is transported to the 3rd fuel supply path 160 being illustrated via cross-drilled hole 158.But, also can directly lubricant oil 102 be transported to the 3rd fuel supply path 160 from the upper end of first fuel supply path 150.
In addition, in embodiments of the present invention 1, the example that is included in the support unit 162 that has elastic force on the vertical direction between the thrust face 130 of bottom race 136 and main bearing 120 is illustrated.But,, also can keep thrust ball bearing 132 supplying lubricating oils 102 and effect that lubricant oil 102 is distributed etc. even under the situation that does not possess support unit 162.
In addition, be equipped with the refrigeration plant of above-mentioned closed type compressor 100, not only can obtain higher efficient, can also guarantee higher reliability.
(mode of execution 2)
Fig. 6 is the longitudinal section of the hermetic type compressor of embodiment of the present invention 2, Fig. 7 is the sectional view of the critical piece on the axle side surface direction of this hermetic type compressor, Fig. 8 is the sectional view of the critical piece of axle on the frontal of this hermetic type compressor, Fig. 9 is the sectional view of the critical piece on the axle side surface direction of this hermetic type compressor, and Figure 10 is the stereogram of the main bearing of this hermetic type compressor.That is be the critical piece of Fig. 9 to be amplified form, at Fig. 7 axis 210.
In Fig. 6～Figure 10, accumulating in seal container 201 has lubricant oil 202, takes in electric element 205 that is made of stator 203 and rotor 204 and the compressing member 206 that is driven by electric element 205.Compressing member 206 comprises axle 210, cylinder block 214, piston 226, linking department 228, main bearing 220 and thrust ball bearing 232.
The main bearing 220 of cylinder block 214 comprises: with the axle center of main bearing 220 generally perpendicularly, the thrust face 230 that forms in the form of a ring; With the bearing extension part 244 that further prolongs upward from thrust face 230, has with main shaft part 211 interior surface opposing.That is, bearing extension part 244 extends to the interior perimembranous of the holding part 233 that constitutes thrust ball bearing 232 described later.In addition, main bearing 220 has the discharge path 268 that is communicated with below vertical direction in the outside of bearing extension part 244.
In addition, at vertical direction upper support axle 210, dispose support unit 262, bottom race 236, a plurality of ball 234 successively and keep the holding part 233 and the top race 235 of ball 234 to upside from the thrust face 230 in the outside of bearing extension part 244.Thereby top race 235 and bottom race 236 are equipped on the upper and lower sides of ball 234 respectively.
And then support unit 262, bottom race 236, a plurality of ball 234 and holding part 233 all are disposed at the outside of bearing extension part 244 in the mode of guaranteeing the radial direction gap.
On the other hand, top race 235 is equipped on the position of more leaning on upside than the upper end 270 of bearing extension part 244.The distance of 234 the topmost part (highly) is longer than the distance (highly) of the upper end 270 from thrust face 230 to bearing extension part 244 from thrust face 230 to ball, utilize this difference in size, between the upper end of bearing extension part 244 and top race 235, be formed with the axle direction gap 246 of regulation.Axle direction gap 246 forms the stream of lubricant oil 202.
Here, support unit 262 is as the bigger wave washer of rigidity or elastic member of hard etc., has elasticity and parts that can resiliently deformable on vertical direction.And, the elastic deformation amount on the vertical direction of support unit 262 is set at bigger than axle direction gap 246.
Then, the detailed structure to the fuel supply path of axle 210 describes.
Therefore, in embodiments of the present invention 2, second fuel supply path 252 is arranged at week in the upper end of bearing extension part 244.In addition, be provided with the plane of inclination of spending with respect to axle center inclination 45 256, thereby realize making the circulation impedance of second fuel supply path 252 to reduce at second fuel supply path 252.
Here, first fuel supply path 250 is made of concentric pump 250a, cross-drilled hole 250b, spiral oil supply 250c.Pump 250a is arranged at the bottom of axle 210 with one heart.Cross-drilled hole 250b is communicated with the top of concentric pump 250a, extends on radial direction.Spiral oil supply 250c, its lower end is communicated with cross-drilled hole 250b at the peripheral part of axle 210, and its upper end is communicated with the plane of inclination 256 of second fuel supply path 252.
In addition, main shaft part 211 also comprises cross-drilled hole 258 and the 3rd fuel supply path 260.Here, the radial direction along main shaft part 211 extends cross-drilled hole 258 from the upper end of spiral oil supply 250c.The 3rd fuel supply path 260, its lower end is communicated with the bottom of cross-drilled hole 258 is neighbouring, extends to the top of eccentric axial portion 212.That is, an end of the 3rd fuel supply path 260 is communicated with first fuel supply path 250.
In order to improve based on the rotation of axle 210 and the conveying capacity of the lubricant oil 202 that produces, the 3rd fuel supply path 260 extends upward along with it, tilt in the mode away from the axle center of main shaft part 211, and the topmost part is at the upper end of eccentric axial portion 212 212a opening.
In addition, in embodiments of the present invention 2, hermetic type compressor 200 employed cold media are to serve as that zero R134a, R600a are that the lower cold naturally medium of warmization coefficient of representative is the cold medium of hydrocarbon class etc. with the ozone layer destroying coefficient, higher with intermiscibility respectively lubricant oil 202 combinations.
Below, the action of the hermetic type compressor 200 that constitutes is as mentioned above described.
The rotor 204 of electric element 205 makes axle 210 rotations, and rotatablely moving of eccentric axial portion 212 is delivered to piston 226 via linking department 228, piston 226 to-and-fro motion in pressing chamber 216 thus.Thus, cold medium is inhaled in the pressing chamber 216 from cooling system (not shown), sprays to cooling system after the compression again.
The weight of axle 210 and rotor 204 is by thrust ball bearing 232 supportings.When axle 210 rotations, owing to ball 234 rolls between top race 235 and bottom race 236, so smooth rotation.
By using thrust ball bearing 232, make the torque ratios of axle 210 rotations not use thrust slide bearing little of ball.Therefore, the hermetic type compressor of embodiment of the present invention 2 can reduce the loss at thrust-bearing, thereby can reduce input, realizes high efficiency.
Then, utilize because the centrifugal force that the rotation of axle 210 produces, by as first fuel supply path 250 that is arranged at a fuel feeding portion 240 of spools 210, the lubricant oil 202 that will accumulate in seal container 201 is drawn onto top from the bottom of main shaft part 211.
Oil stream (the representing) 261 that will be assigned as the oil stream (representing) 251 that flows to second fuel supply path 252 by the lubricant oil 202 that first fuel supply path 250 is transported to the top of main shaft part 211 and flow to the 3rd fuel supply path 260 with arrow with arrow.Here, the oil stream 251 that flows to second fuel supply path 252 is the lubricant oil 202 that passes through plane of inclination 256 from the predetermined distance a that constitutes second fuel supply path 252, is fed to the oil stream of the lubricant oil 202 of thrust ball bearing 232 via circumferential groove 252a.The oil stream 261 that flows to the 3rd fuel supply path 260 is that the oil of the lubricant oil 202 of lubricant oil 202 top that fed to eccentric axial portion 212 via cross-drilled hole 258 flows.
Owing between the upper end of bearing extension part 244 and top race 235, be formed with the axle direction gap 246 of regulation, therefore the oil stream 251 that flows to second fuel supply path 252 flows on radial direction via axle direction gap 246, forms the oil stream towards thrust ball bearing 232.
Particularly, this oil stream 251 that flows to second fuel supply path 252 forms the oil stream at the rolling position that directly flows to ball 234 and top race 235, thereby is reduced in the loss of ball 234 and top race 235 effectively.In addition, the oil stream 251 that flows to second fuel supply path 252 can reduce heat release, prevent to produce owing to what lack of lubrication caused and peel off equivalent damage.
And then, by changing the size in axle direction gap 246, can change the stream impedance of the oil stream 251 that flows to second fuel supply path 252.In addition, flow to the stream impedance of the oil stream 251 of second fuel supply path 252 by increase, lubricant oil 202 flows of the oil stream 261 that flows to the 3rd fuel supply path 260 are increased, perhaps on the contrary, the stream impedance of the oil stream 251 by reducing to flow to second fuel supply path 252 can make lubricant oil 202 flows of the oil stream 261 that flows to the 3rd fuel supply path reduce.
Therefore, the lubricant oil 202 that is transported to the top of main shaft part 211 by first fuel supply path 250 can be become to flow to the oil stream (flowing to the oil stream 251 of second fuel supply path 252) of the lubricant oil 202 of thrust ball bearing 232 according to the pro rate of expectation and flow to the oil stream (flowing to the oil stream 261 of the 3rd fuel supply path 260) of lubricant oil 202 of the top of eccentric axial portion 212.In addition, the flow that is fed to the lubricant oil 202 of thrust ball bearing 232 can be adjusted into the best.
Therefore, lubricant oil 202 is fed to thrust ball bearing 232 and eccentric axial portion 212 according to optimal flow rate.Therefore, the hermetic type compressor of embodiment of the present invention 2 can reduce the slip loss, and can reduce heat release, prevents to produce owing to what lack of lubrication caused and peel off equivalent damage, thereby obtains higher reliability.
In addition, best distribution also can similarly be carried out to above-mentioned lubricant oil 202 in the size of space of the predetermined distance 270 by setting second fuel supply path 252 and the angle of inclination of plane of inclination 256 etc.
That is, by changing sectional area, stream impedance and the angle of inclination etc. of plane of inclination 256, even do not change the stream impedance that axle direction gap 246 also can change the oil stream 251 that flows to second fuel supply path 252.And, flow to the stream impedance of the oil stream 251 of second fuel supply path 252 by increase, lubricant oil 202 flows of the oil stream 261 that flows to the 3rd fuel supply path 260 are increased, perhaps on the contrary, the stream impedance of the oil stream 251 by reducing to flow to second fuel supply path 252 can make lubricant oil 202 flows of the oil stream 261 that flows to the 3rd fuel supply path 260 reduce.Like this, by changing the stream impedance of second fuel supply path 252, also can adjust the flow of the lubricant oil 202 in interior week of being fed to thrust ball bearing 232.
In addition, second fuel supply path 252 is not simple communication paths, and it comprises: the part of opening periphery that will be arranged at the cross-drilled hole 258 of main shaft part 211 eliminates and the predetermined distance 270 that forms; With week in the upper end that is arranged at bearing extension part 244, with respect to the plane of inclination 256 that 45 degree form that tilts, axle center.Therefore, effectively utilize centrifugal force, 256 inclination is directed at the upper end of bearing extension part 244 swimmingly along the plane of inclination with the lubricant oil 202 of lower end that is transported to plane of inclination 256, supplies with thrust ball bearing 232.
In addition, also can adjust the flow of lubricant oil 202 by the stream impedance that changes axle direction gap 246 and plane of inclination 256 and predetermined distance 270.Consequently, can distribute the oil stream (flowing to the oil stream 251 of second fuel supply path) of the lubricant oil 202 that flows to thrust ball bearing 232 and the oil stream (flowing to the oil stream 261 of the 3rd fuel supply path 260) of lubricant oil 202 that flows to the top of eccentric axial portion 212 according to the ratio of very refinement.
Then, in carrying during hermetic type compressor 200 etc., exist owing to the situation that impact load on the vertical direction that produces acts on electric element 205 and compressing member 206 such as falling.At this moment, the load on the vertical direction also acts on thrust ball bearing 232, and the support unit 262 that makes it possible to resiliently deformable produces resiliently deformable.That is, in support unit 262 can the deformation band of resiliently deformable, the axle direction gap 246 between the upper end of bearing extension part 244 and the top race 235 became zero, formed butt.This is because than axle direction gap 246 big modes the elastic deformation amount of support unit 262 on vertical direction set.
Like this, the impact load on vertical direction is done the time spent, is not thrust ball bearing 232 but upper end and top race 235 butts by bearing extension part 244 support this load, thereby can supports impact load.Therefore, the contact load that can prevent ball 234, top race 235 and bottom race 236 increases to extremely.
Consequently, the plastic deformation of thrust ball bearing 232 can be prevented, the slip of thrust ball bearing 232 can be maintained good state, so the hermetic type compressor of embodiment of the present invention 2 low noise, high efficiency and high reliability can be obtained.
Then, the oily stream to the lubricant oil 202 that fed to thrust ball bearing 232 illustrates.
After thrust ball bearing 232 was lubricated, the lubricant oil 202 that is fed to thrust ball bearing 232 can be accumulated in the outside of bearing extension part 244, made that thrust ball bearing 232 is soaked.Yet lubricant oil 202 can be via the discharge path 268 that is arranged at cylinder block 214, and the utilization deadweight is discharged to the space in the seal container 201.
Therefore, can always supply with new lubricant oil 202 circularly, and can prevent that it from accumulating to thrust ball bearing 232.Consequently, the hermetic type compressor of embodiment of the present invention 2 can prevent the accumulation of abrasion powder etc., thereby can obtain higher reliability.
In addition, in present embodiment 2, the example that possesses second fuel supply path 252 is illustrated.Yet, also can only pass through axle direction gap 246, become to flow to the oil stream (flowing to the oil stream 251 of second fuel supply path) of the lubricant oil 202 of thrust ball bearing 232 and flow to the oil stream (flowing to the oil stream 261 of the 3rd fuel supply path 260) of lubricant oil 202 of the top of eccentric axial portion 212 according to the pro rate of expectation.
In addition, to the situation as second fuel supply path 252 is illustrated to extend along axle direction in the plane of inclination 256 of the peripheral part of main shaft part 211, still, also can be the groove of other shapes, the fuel supply path of other modes.
In addition, in embodiments of the present invention 2, the example that discharge path 268 is arranged at cylinder block 214 is illustrated.But, if can be, after thrust ball bearing 232 is lubricated, it be discharged to the space in the seal container 201 according to the mode that always new lubricant oil 202 can be fed to circularly thrust ball bearing 232, then also can be other structure.
In addition, in embodiments of the present invention 2, to the example that lubricant oil 202 is transported to the 3rd fuel supply path 260 being illustrated via cross-drilled hole 258.But, also can directly lubricant oil 202 be transported to the 3rd fuel supply path 260 from the upper end of first fuel supply path 250.
In addition, in embodiments of the present invention 2, the example that is included in the support unit 262 that has elastic force on the vertical direction between the thrust face 230 of bottom race 236 and main bearing 220 is illustrated.But,, also can keep thrust ball bearing 232 supplying lubricating oils 202 and effect that lubricant oil 202 is distributed etc. even under the situation that does not possess support unit 262.
In addition, be equipped with the refrigeration plant of above-mentioned hermetic type compressor 200, not only can obtain higher efficient, can also guarantee higher reliability.
(mode of execution 3)
Figure 11 is the longitudinal section of the hermetic type compressor of embodiment of the present invention 3, Figure 12 is the sectional view of the critical piece on the axle side surface direction of this hermetic type compressor, Figure 13 is the sectional view of the critical piece of axle on the frontal of this hermetic type compressor, Figure 14 is the sectional view of the critical piece on the axle side surface direction of this hermetic type compressor, and Figure 15 is the stereogram of the main bearing of this hermetic type compressor.That is be the critical piece of Figure 14 to be amplified form, at Figure 12 axis 310.
In Figure 11～Figure 15, accumulating in seal container 301 has lubricant oil 302, takes in electric element 305 that is made of stator 303 and rotor 304 and the compressing member 306 that is driven by electric element 305.Compressing member 306 comprises axle 310, cylinder block 314, piston 326, linking department 328, main bearing 320 and thrust ball bearing 332.
Cylinder block 314 is formed with the pressing chamber 316 of general cylindrical shape.In addition, be fixed with the main bearing 320 that forms cantilever bearings by axle supporting spindle portion 311 at cylinder block 314.Piston 326 is inserted in the pressing chamber 316 of cylinder block 314 in the mode freely of can reciprocatingly sliding.Link by linking department 328 between piston 326 and the eccentric axial portion 212.
The main bearing 320 of cylinder block 314 comprises: with the axle center of main bearing 320 generally perpendicularly, the thrust face 330 that forms in the form of a ring; With the bearing extension part 344 that further prolongs upward from thrust face 330, has with main shaft part 311 interior surface opposing.That is, bearing extension part 344 extends to the interior perimembranous of the holding part 333 that constitutes thrust ball bearing 332 described later.In addition, main bearing 320 has the discharge path 368 that is communicated with below vertical direction in the outside of bearing extension part 344.
In addition, at vertical direction upper support axle 310, dispose support unit 362, bottom race 336, a plurality of ball 334 successively and keep the holding part 333 and the top race 335 of ball 334 to upside from the thrust face 330 in the outside of bearing extension part 344.Therefore, top race 335 and bottom race 336 are equipped on the upper and lower sides of ball 334 respectively.
And then support unit 362, bottom race 336, a plurality of ball 334 and holding part 333 all are disposed at the outside of bearing extension part 344 in the mode of guaranteeing the radial direction gap.
On the other hand, top race 335 is equipped on the position of more leaning on upside than the upper end 370 of bearing extension part 344.The distance of 334 the topmost part (highly) is longer than the distance (highly) of the upper end 370 from thrust face 330 to bearing extension part 344 from thrust face 330 to ball, utilize this difference in size, between the upper end of bearing extension part 344 and top race 335, be formed with the axle direction gap 346 of regulation.Axle direction gap 346 forms the stream of lubricant oil 302.
Here, support unit 362 is as the bigger wave washer of rigidity or elastic member of hard etc., has elasticity and parts that can resiliently deformable on vertical direction.And, the elastic deformation amount on the vertical direction of support unit 362 is set at bigger than axle direction gap 346.
Then, the detailed structure to the fuel supply path of axle 310 describes.
Here, first fuel supply path 350 is made of concentric pump 350a, cross-drilled hole 350b, spiral oil supply 350c.Pump 350a is arranged at the bottom of axle 310 with one heart.Cross-drilled hole 350b is communicated with the top of concentric pump 350a, extends on radial direction.Spiral oil supply 350c, its lower end is communicated with cross-drilled hole 350b at the peripheral part of axle 310, and its upper end is communicated with the groove 354 of the slit-shaped of second fuel supply path 352.
In addition, on radial direction,, be provided with in mode relative with bearing extension part 344 on the general horizontal direction of ball 334 with the 4th fuel supply path 366 that is communicated with in interior week of bearing extension part 344 with periphery.
In addition, main shaft part 311 also comprises cross-drilled hole 358 and the 3rd fuel supply path 360.Here, the radial direction along main shaft part 311 extends cross-drilled hole 358 from the upper end of spiral oil supply 350c.The 3rd fuel supply path 360, its lower end is communicated with the bottom of cross-drilled hole 358 is neighbouring, extends to the top of eccentric axial portion 312.That is, an end of the 3rd fuel supply path 360 is communicated with first fuel supply path 350.
In order to improve based on the rotation of axle 310 and the conveying capacity of the lubricant oil 302 that produces, the 3rd fuel supply path 360 extends upward along with it, tilt in the mode away from the axle center of main shaft part 311, and the topmost part is at the upper end of eccentric axial portion 312 312a opening.
In addition, in present embodiment 3, hermetic type compressor 300 employed cold media are to serve as that zero R134a, R600a are that the lower cold naturally medium of warmization coefficient of representative is the cold medium of hydrocarbon class etc. with the ozone layer destroying coefficient, higher with intermiscibility respectively lubricant oil 302 combinations.
Below, the action of the hermetic type compressor 300 that constitutes is as mentioned above described.
The rotor 304 of electric element 305 makes axle 310 rotations, and rotatablely moving of eccentric axial portion 312 is delivered to piston 326 via linking department 328, piston 326 to-and-fro motion in pressing chamber 316 thus.Thus, cold medium is inhaled in the pressing chamber 316 from cooling system (not shown), sprays to cooling system after the compression again.
The weight of axle 310 and rotor 304 is by thrust ball bearing 332 supportings.In addition, when axle 310 rotations, owing to ball 334 rolls between top race 335 and bottom race 336, so smooth rotation.
By using thrust ball bearing 332, make the torque ratios of axle 310 rotations not use thrust slide bearing little of ball.Therefore, the hermetic type compressor of embodiment of the present invention 3 can reduce the loss at thrust-bearing, thereby can reduce input, realizes high efficiency.
Then, utilize because the centrifugal force that the rotation of axle 310 produces, by as first fuel supply path 350 that is arranged at a fuel feeding portion 340 of spools 310, the lubricant oil 302 that will accumulate in seal container 301 is drawn onto top from the bottom of main shaft part 311.
Oil stream (the representing) 361 that will be distributed into the oil stream (representing) 351 that flows to second fuel supply path 352 by the lubricant oil 302 that first fuel supply path 350 is transported to the top of main shaft part 311 and flow to the 3rd fuel supply path 360 with arrow with arrow.Here, the oil stream 351 that flows to second fuel supply path 352 is the lubricant oil 302 by the groove 354 of slit-shaped, is fed to the oil stream of the lubricant oil 302 of thrust ball bearing 332 via circumferential groove 352a.The oil stream 361 that flows to the 3rd fuel supply path 360 is that the oil of the lubricant oil 302 of lubricant oil 302 top that fed to eccentric axial portion 312 via cross-drilled hole 358 flows.
Owing between the upper end of bearing extension part 344 and top race 335, be formed with the axle direction gap 346 of regulation, therefore the oil stream 351 that flows to second fuel supply path 352 flows on radial direction via axle direction gap 346, forms the oil stream towards thrust ball bearing 332.
Particularly, this oil stream 351 that flows to second fuel supply path 352 forms the oil stream at the rolling position that directly flows to ball 334 and top race 335, thereby is reduced in the loss of ball 334 and top race 335 effectively.In addition, the oil stream 351 that flows to second fuel supply path 352 can reduce heat release, prevent to produce owing to what lack of lubrication caused and peel off equivalent damage.
And then, by changing the size in axle direction gap 346, can change the stream impedance of the oil stream 351 that flows to second fuel supply path 352.In addition, flow to the stream impedance of the oil stream 351 of second fuel supply path 352 by increase, lubricant oil 302 flows of the oil stream 361 that flows to the 3rd fuel supply path 360 are increased, perhaps on the contrary, the stream impedance of the oil stream 351 by reducing to flow to second fuel supply path 352 can make lubricant oil 302 flows of the oil stream 361 that flows to the 3rd fuel supply path 360 reduce.
Therefore, the lubricant oil 302 that is transported to the top of main shaft part 311 by first fuel supply path 350 can be become to flow to the oil stream (flowing to the oil stream 351 of second fuel supply path 352) of the lubricant oil 302 of thrust ball bearing 332 according to the pro rate of expectation and flow to the oil stream (flowing to the oil stream 361 of the 3rd fuel supply path 360) of lubricant oil 302 of the top of eccentric axial portion 312.In addition, the flow that is fed to the lubricant oil 302 of thrust ball bearing 332 can be adjusted into the best.That is, by changing the stream impedance of second fuel supply path 352, the flow of the lubricant oil 302 in interior week of being fed to thrust ball bearing 332 is adjusted.
Therefore, lubricant oil 302 is fed to thrust ball bearing 332 and eccentric axial portion 312 with optimal flow rate.Therefore, the hermetic type compressor of embodiment of the present invention 3 can reduce the slip loss, and can reduce heat release, prevents to produce owing to what lack of lubrication caused and peel off equivalent damage, thereby obtains higher reliability.
In addition, utilize the groove 354 of the slit-shaped of second fuel supply path 352 also can similarly implement best distribution to above-mentioned lubricant oil 302.
That is, the section area of the groove 354 by changing slit-shaped is not even change the stream impedance that axle direction gap 346 also can change the oil stream 351 that flows to second fuel supply path 352.And, flow to the stream impedance of the oil stream 351 of second fuel supply path 352 by increase, lubricant oil 302 flows of the oil stream 361 that flows to the 3rd fuel supply path 360 are increased, perhaps on the contrary, the stream impedance of the oil stream 351 by reducing to flow to second fuel supply path 352 can make lubricant oil 302 flows of the oil stream 361 that flows to the 3rd fuel supply path reduce.Like this, by changing the stream impedance of second fuel supply path 352, also can adjust the flow of the lubricant oil 302 in interior week of being fed to thrust ball bearing 332.
In addition, the section area of groove 354 that also can be by changing axle direction gap 346 and slit-shaped is adjusted the flow of lubricant oil 302.Consequently, can distribute the oil stream (flowing to the oil stream 351 of second fuel supply path 352) of the lubricant oil 302 that flows to thrust ball bearing 332 and the oil stream (flowing to the oil stream 361 of the 3rd fuel supply path 360) of lubricant oil 302 that flows to the top of eccentric axial portion 312 according to the ratio of very refinement.
And then, in present embodiment 3, constitute at bearing extension part 344 and be provided with the 4th fuel supply path 366.
This structure is: along with the rotation of axle 310, the groove 354 of the slit-shaped of second fuel supply path 352 and the 4th fuel supply path 366 are communicated with discontinuously.Consequently, can be not via axle direction gap 346 to thrust ball bearing 332 supplying lubricating oil 302 discontinuously.
Therefore, particularly the gasiform cold medium that is blended in the lubricant oil 302 that is fed to second fuel supply path 352 early can be discharged in the seal container 301, thereby prevent that the fuel feeding that is caused by the cold medium that aerifies from hindering.
And then, via the 4th fuel supply path 366, can be to ball 334 integral body of thrust ball bearing 332 supplying lubricating oil 302 fully.Therefore, the hermetic type compressor of embodiment of the present invention 3 can further reduce the slip loss, and can reduce heat release, prevents to produce owing to what lack of lubrication caused and peel off equivalent damage, thereby obtains higher reliability.
Then, in carrying during hermetic type compressor 300 etc., exist owing to the situation that impact load on the vertical direction that produces acts on electric element 305 and compressing member 306 such as falling.At this moment, the load on the vertical direction also acts on thrust ball bearing 332, and the support unit 362 that makes it possible to resiliently deformable produces resiliently deformable.That is, in support unit 362 can the deformation band of resiliently deformable, the axle direction gap 346 between the upper end of bearing extension part 344 and the top race 335 became zero, formed butt.This is because than axle direction gap 346 big modes the elastic deformation amount of support unit 362 on vertical direction set.
Like this, the impact load on vertical direction is done the time spent, is not thrust ball bearing 332 but upper end and top race 335 butts by bearing extension part 344 support this load, thereby can supports impact load.Therefore, can prevent that the contact load increase of ball 334, top race 335 and bottom race 336 is for extreme.
Consequently, the plastic deformation of thrust ball bearing 332 can be prevented, the slip of thrust ball bearing 332 can be maintained good state, so the hermetic type compressor of embodiment of the present invention 3 low noise, high efficiency and high reliability can be obtained.
Then, the oily stream to the lubricant oil 302 that fed to thrust ball bearing 332 illustrates.
After thrust ball bearing 332 was lubricated, the lubricant oil 302 that is fed to thrust ball bearing 332 can be accumulated in the outside of bearing extension part 344, made that thrust ball bearing 332 is soaked.Yet lubricant oil 302 can be via the discharge path 368 that is arranged at cylinder block 314, and the utilization deadweight is discharged to the space in the seal container 301.
Therefore, can always supply with new lubricant oil 302 circularly, and can prevent that it from accumulating to thrust ball bearing 332.Consequently, the hermetic type compressor of embodiment of the present invention 3 can prevent the accumulation of abrasion powder etc., thereby can obtain higher reliability.
In addition, in present embodiment 3, the example that possesses second fuel supply path 352 is illustrated.Yet, also can only pass through axle direction gap 346, become to flow to the oil stream (flowing to the oil stream 351 of second fuel supply path 352) of the lubricant oil 302 of thrust ball bearing 332 and flow to the oil stream (flowing to the oil stream 361 of the 3rd fuel supply path 360) of lubricant oil 302 of the top of eccentric axial portion 312 according to the pro rate of expectation.
In addition, to being illustrated, but also can be the groove of other shapes, the fuel supply path of other modes to extend along axle direction in the groove 354 of the slit-shaped of the peripheral part of main shaft part 311 situation as second fuel supply path 352.
In addition, in embodiments of the present invention 3, the example that discharge path 368 is arranged at cylinder block 314 is illustrated.But, if can be, after thrust ball bearing 332 is lubricated, it be discharged to the space in the seal container 301 according to the mode that always new lubricant oil 302 can be fed to circularly thrust ball bearing 332, then also can be other structure.
In addition, in embodiments of the present invention 3, to the example that lubricant oil 302 is transported to the 3rd fuel supply path 360 being illustrated via cross-drilled hole 358.But, also can directly lubricant oil 302 be transported to the 3rd fuel supply path 360 from the upper end of first fuel supply path 350.
In addition, in embodiments of the present invention 3, the example that is included in the support unit 362 that has elastic force on the vertical direction between the thrust face 330 of bottom race 336 and main bearing 320 is illustrated.But,, also can keep thrust ball bearing 332 supplying lubricating oils 302 and effect that lubricant oil 302 is distributed etc. even under the situation that does not possess support unit 362.
In addition, Figure 16 is the refrigeration plant of embodiment of the present invention 3.Be equipped with the refrigeration plant 380 of above-mentioned hermetic type compressor 300, not only can obtain higher efficient, can also guarantee higher reliability.
Claims (10)
1. hermetic type compressor is characterized in that:
Accumulating in seal container has lubricant oil, and takes in electric element that possesses stator and rotor and the compressing member that is driven by described electric element,
Described compressing member comprises:
Axle with the main shaft part of on vertical direction, extending and eccentric axial portion;
Form the cylinder block of columnar pressing chamber;
Can be inserted in the piston of described pressing chamber inside in reciprocating mode;
The linking department that links described piston and described eccentric axial portion;
Be arranged at described cylinder block, support the main bearing that described main shaft part forms cantilever bearings by axle; With
Thrust ball bearing, this thrust ball bearing have the thrust face that is equipped on described main bearing and a plurality of balls that kept by holding part and top race and the bottom race that is equipped on the upper and lower sides of described ball respectively,
Described axle has from the peripheral part of the described axle fuel feeding portion that supplies with described lubricant oil interior week to described thrust ball bearing, interior perimembranous in described holding part is equipped with the bearing extension part that described main bearing extension forms, and be provided with the axle direction gap between the upper end of described bearing extension part and described top race, described axle direction gap forms the stream of described lubricant oil.
2. hermetic type compressor as claimed in claim 1 is characterized in that:
Described fuel feeding portion has: first fuel supply path that described lubricant oil is transported to top from the bottom of described main shaft part; With second fuel supply path that an end is communicated with the upper end of described first fuel supply path, the other end is communicated with the upper end of described bearing extension part, by changing the stream impedance of described second fuel supply path, the described flow rate of lubricating oil in interior week of being fed to described thrust ball bearing is adjusted.
3. hermetic type compressor as claimed in claim 2 is characterized in that:
Described second fuel supply path is the groove of slit-shaped, and the groove of described slit-shaped extends peripheral part in described main shaft part along vertical direction.
4. hermetic type compressor as claimed in claim 2 is characterized in that:
Described second fuel supply path is the plane of inclination that is arranged at week in the upper end of described bearing extension part.
5. as each described hermetic type compressor in the claim 2～4, it is characterized in that:
Described main shaft part possesses the 3rd fuel supply path that an end and described first fuel supply path are communicated with and extend to the top of described eccentric axial portion, by changing the stream impedance of described second fuel supply path, the described lubricant oil that will be carried by described first fuel supply path becomes flow to the oil stream of described second fuel supply path according to the pro rate of expectation and flows to the oil stream of described the 3rd fuel supply path.
6. hermetic type compressor as claimed in claim 1 is characterized in that:
Between described bottom race and described thrust face, possesses the support unit that on vertical direction, has elastic force.
7. hermetic type compressor as claimed in claim 6 is characterized in that:
By forming described axle direction gap in the mode littler than the elastic deformation amount of described support unit, the impact load on vertical direction is done the time spent, and the upper end of described bearing extension part and described top race butt support impact load.
8. hermetic type compressor as claimed in claim 1 is characterized in that:
Described bearing extension part possesses the interior week of the described bearing extension part of connection on radial direction and the 4th fuel supply path of periphery.
9. hermetic type compressor as claimed in claim 1 is characterized in that:
Possess and to be lubricated the discharge path that described lubricant oil afterwards is discharged to the space in the described seal container to described thrust ball bearing.
10. refrigeration plant is characterized in that:
Be equipped with the described hermetic type compressor of claim 1.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009-107579 | 2009-04-27 | ||
| JP2009107579A JP5353414B2 (en) | 2009-04-27 | 2009-04-27 | Hermetic compressor and refrigeration system |
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| Publication Number | Publication Date |
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| CN101871443A true CN101871443A (en) | 2010-10-27 |
| CN101871443B CN101871443B (en) | 2013-04-10 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN 201010167333 Active CN101871443B (en) | 2009-04-27 | 2010-04-27 | Enclosed compressor and refrigeration device |
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| JP (1) | JP5353414B2 (en) |
| CN (1) | CN101871443B (en) |
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- 2009-04-27 JP JP2009107579A patent/JP5353414B2/en active Active
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2010
- 2010-04-27 CN CN 201010167333 patent/CN101871443B/en active Active
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Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103987965A (en) * | 2011-12-27 | 2014-08-13 | 松下电器产业株式会社 | Hermetic compressor and refrigerator with the same |
| CN104114864A (en) * | 2012-03-16 | 2014-10-22 | 松下电器产业株式会社 | Hermetically sealed compressor, and freezing device provided therewith |
| CN104169580A (en) * | 2012-04-12 | 2014-11-26 | 松下电器产业株式会社 | Hermetic compressor and refrigeration device comprising same |
| CN104379930A (en) * | 2012-06-13 | 2015-02-25 | 松下知识产权经营株式会社 | Hermetic compressor |
| CN104379930B (en) * | 2012-06-13 | 2016-11-09 | 松下知识产权经营株式会社 | Hermetic type compressor |
| US9617986B2 (en) | 2012-06-13 | 2017-04-11 | Panasonic Intellectual Property Management Co., Ltd. | Hermetic compressor |
| CN105715511A (en) * | 2014-12-18 | 2016-06-29 | Lg电子株式会社 | Compressor |
| CN105715511B (en) * | 2014-12-18 | 2018-03-23 | Lg电子株式会社 | Compressor |
| US10859076B2 (en) | 2014-12-18 | 2020-12-08 | Lg Electronics Inc. | Compressor |
| WO2017012098A1 (en) * | 2015-07-17 | 2017-01-26 | 安徽美芝制冷设备有限公司 | Piston compressor and refrigerating system having same |
| CN111788394A (en) * | 2018-03-05 | 2020-10-16 | 三菱电机株式会社 | Compressor with a compressor housing having a plurality of compressor blades |
| CN114131356A (en) * | 2021-12-31 | 2022-03-04 | 姜堰经济开发区科创中心 | High-precision liquid static pressure bearing B-axis turntable device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2010255556A (en) | 2010-11-11 |
| CN101871443B (en) | 2013-04-10 |
| JP5353414B2 (en) | 2013-11-27 |
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Effective date of registration: 20180507 Address after: Singapore Bedok South 1 Street Patentee after: Panasonic refrigeration plant Singapore Address before: Osaka Japan Patentee before: Matsushita Electric Industrial Co., Ltd. |