CN201818470U - Closed type compressor - Google Patents
Closed type compressor Download PDFInfo
- Publication number
- CN201818470U CN201818470U CN2010205896728U CN201020589672U CN201818470U CN 201818470 U CN201818470 U CN 201818470U CN 2010205896728 U CN2010205896728 U CN 2010205896728U CN 201020589672 U CN201020589672 U CN 201020589672U CN 201818470 U CN201818470 U CN 201818470U
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- axial portion
- piston
- eccentric axial
- cylinder block
- lubricant oil
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- 239000000314 lubricant Substances 0.000 claims description 79
- 230000007246 mechanism Effects 0.000 claims description 33
- 239000000446 fuel Substances 0.000 claims description 29
- 238000003825 pressing Methods 0.000 claims description 28
- 238000003754 machining Methods 0.000 claims description 5
- 239000003921 oil Substances 0.000 abstract description 97
- 238000007789 sealing Methods 0.000 abstract description 16
- 239000010687 lubricating oil Substances 0.000 abstract description 5
- 238000005057 refrigeration Methods 0.000 description 15
- 239000003795 chemical substances by application Substances 0.000 description 11
- 238000001816 cooling Methods 0.000 description 11
- 230000000694 effects Effects 0.000 description 7
- 238000000034 method Methods 0.000 description 7
- 230000009467 reduction Effects 0.000 description 6
- 239000003507 refrigerant Substances 0.000 description 6
- 210000000707 wrist Anatomy 0.000 description 6
- 230000009471 action Effects 0.000 description 5
- 230000006835 compression Effects 0.000 description 5
- 238000007906 compression Methods 0.000 description 5
- 239000007921 spray Substances 0.000 description 5
- 239000004215 Carbon black (E152) Substances 0.000 description 4
- 229930195733 hydrocarbon Natural products 0.000 description 4
- 150000002430 hydrocarbons Chemical class 0.000 description 4
- NNPPMTNAJDCUHE-UHFFFAOYSA-N isobutane Chemical compound CC(C)C NNPPMTNAJDCUHE-UHFFFAOYSA-N 0.000 description 4
- 230000008569 process Effects 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000009826 distribution Methods 0.000 description 2
- 239000001282 iso-butane Substances 0.000 description 2
- 230000005855 radiation Effects 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 238000010792 warming Methods 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 239000000853 adhesive Substances 0.000 description 1
- 230000001070 adhesive effect Effects 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 230000007306 turnover Effects 0.000 description 1
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Abstract
The utility model provides a closed type compressor, wherein a lubricating oil discharge hole is arranged at the upper end of an eccentric shaft of a crankshaft. The opening of the lubricating oil discharge hole is at the relative height on the back side of a piston.In addition, an oil-collecting portion is arranged above the front of the upper end of the eccentric shaft of the crankshaft in the cylinder block.As a result, lubricating oil sprayed out of the upper end of the eccentric shaft of the crankshaft reliably runs into the oil-collecting portion to provide oil at the upper portion of the piston.Oil is also provided at the back side of the piston through the lubricating oil discharge hole, thereby ensuring the sealing performance of the cylinder block and the piston and improving the efficiency and reliability of the compressor.
Description
Technical field
The present invention relates to the hermetic type compressor that in the cooling cycle system device of refrigerator refrigerator etc., uses.
Background technique
In recent years, the hermetic type compressor that uses in the cooling cycle system device of family expenses refrigerator refrigerator, vending machine, air-conditioning etc. requires high efficiency and high reliability.Therefore, in the hermetic type compressor of prior art,, efficient and reliability are improved by improving the fuel feeding path, lubricant oil being sprayed, supplies with to piston top more reliably.Such hermetic type compressor is for example open in TOHKEMY 2003-065236 communique.
Following limit describes with reference to the hermetic type compressor of accompanying drawing limit to prior art.Fig. 8 is the longitudinal section of the hermetic type compressor of prior art.Fig. 9 is the sectional view after amplify on the top of hermetic type compressor shown in Figure 8.
The inner space 2 of seal container 1 contains motor drive mechanism 5, compressing mechanism 6 and lubricant oil 7.Motor drive mechanism 5 has stator 3 and is built-in with the rotor 4 of permanent magnet.Motor drive mechanism 5 drives with a plurality of operating frequencys that comprise less than the revolution of industrial power frequency by inverter driving dynamic control device (not shown).Compressing mechanism 6 drives by motor drive mechanism 5.Lubricant oil 7 is stored in the bottom in the seal container 1.In addition, in the inner space 2 of seal container 1 filling representative hydrocarbon refrigerant R600a (isobutane) in the low natural refrigeration agent of global warming coefficient.
The block 15 that constitutes compressing mechanism 6 has cylinder block 16 that forms columnar pressing chamber 17 and the main bearing portion 18 that supports the main shaft part 9 of bent axle 8.Be inserted with the piston 19 that can freely reciprocatingly slide in the pressing chamber 17.Piston 19 links to each other with joint 20 by wrist pin 22, and joint 20 is connected with the eccentric axial portion 10 of bent axle 8.In the upper wall portions of pressing chamber 17,, be provided with the notch part 21 of semicircular arc in order to insert wrist pin 22.The eccentric axial portion 10 of bent axle 8 is formed on the position with respect to main shaft part 9 off-centre.In main shaft part 9, be pressed into the rotor 4 that is fixed with motor drive mechanism 5.
The 8a of fuel feeding portion that is formed on bent axle 8 is made of viscosity pump 12, heeling pump 11, attachment hole 13 and lubricant oil bleed hole 14.Viscosity pump 12 is formed on the surface of bent axle 8, and towards the axle direction spiral extension.Heeling pump 11 is formed on the bottom of bent axle 8.One end of heeling pump 11 is at lubricant oil 7 split sheds, and the other end is communicated with viscosity pump 12.Attachment hole 13 is set at eccentric axial portion 10.One end of attachment hole 13 is communicated with the upper end of viscosity pump 12, the space 2 of the other end in the seal container 1, opening upward.One end of lubricant oil bleed hole 14 is communicated with attachment hole 13, and the other end is at the outer circumferential face opening of eccentric axial portion 10.Lubricant oil bleed hole 14 is arranged on when eccentric axial portion 10 height and position relative with notch part 21 during near pressing chamber 17.
Next the working method of the hermetic type compressor of aforesaid structure is described.The rotor 4 of motor drive mechanism 5 rotates bent axle 8, is accompanied by this and rotates, and rotatablely moving of eccentric axial portion 10 passed to piston 19 by joint 20 and wrist pin 22.Therefore, piston 19 moves back and forth in pressing chamber 17.Thus, be inhaled in the pressing chamber 17, after being compressed, be ejected into refrigeration system once more here from the refrigerant gas of refrigeration system (not shown).Then repeat this circulation.
Be accompanied by the rotation of bent axle 8 in addition, the lubricant oil 7 in the heeling pump 11 is supplied with each slide part because centrifugal force is pumped to the top by viscosity pump 12.Then, lubricant oil 7 is drawn into the attachment hole 13 in the interior week that is arranged on eccentric axial portion 10, emits (distribution) from the upper end and the lubricant oil bleed hole 14 of attachment hole 13 along circumferencial direction.In attachment hole 13, lubricant oil 7 is in eccentric direction partially because of the centrifugal force of the rotation of following eccentric axial portion 10.So when piston 19 was in the state that near the cylinder block 16 being positioned at lower dead centre exposes, the lubricant oil 7 of emitting from lubricant oil bleed hole 14 collided with the notch part 21 of semicircular arc, scatters out above piston 19.
Consequently, between piston 19 and cylinder block 16, can supply with the lubricant oil 7 of q.s.Consequently, this makes volumetric efficiency rise owing to sealing is high between the two, and the efficient of hermetic type compressor rises.In addition, by simultaneously and the fuel feeding of capacity can reduce friction between piston 19 and the cylinder block 16.
Structure hereto, as the compressor that uses hydrocarbon refrigerant R600a, when the inflator volume becomes big, the position that needs to cooperate the external diameter of cylinder block 16 and piston 19 to improve the lubricant oil bleed hole 14 that is arranged on bent axle 8.But when the external diameter of fitting piston 19 improved the position of lubricant oil bleed hole 14, it is big that eccentric axial portion 10 can become, and the necessity that increases seal container 1 is consequently arranged.
In addition, along with the high capacity of inflator volume, the heating value of compressing mechanism 6 increases, and brings the temperature rising of lubricant oil 7, the viscosity of lubricant oil 7 to reduce thus, makes that the sealing between piston 19 and the cylinder block 16 becomes insufficient.In addition, the cooling action of sliding parts also can descend, and the reliability of compressor may reduce.
Summary of the invention
The present invention is a kind of hermetic type compressor, even if its inflator volume also can allow lubricant oil reasonably disperse above piston greatly, guarantees the sealing between piston and the cylinder block, makes because of the raising of the cooling action of piston that in addition reliability improves.
Hermetic type compressor of the present invention has seal container, is housed in the interior motor drive mechanism with stator and rotor of seal container, is housed in the compressing mechanism in the seal container.Compressing mechanism has bent axle, cylinder block, piston and joint.Bent axle is made up of main shaft part and the eccentric axial portion that is arranged on the main shaft part top.Upper end in eccentric axial portion is formed with attachment hole, and the radial direction from attachment hole along eccentric axial portion is formed with the lubricant oil bleed hole of perforation.First end of bent axle is in the lower openings of main shaft part in addition, and second end has the fuel feeding portion that is communicated with attachment hole.The cylinder block is with the mode supports main shaft portion that can freely rotate and have pressing chamber.Contain the piston that can move reciprocatingly in the pressing chamber.Joint is connected eccentric axial portion with piston.The main shaft part of bent axle combines with the rotor of motor drive mechanism.At the upper wall of the pressing chamber of cylinder block, be provided with the notch part of semicircular arc.The lubricant oil bleed hole is set at the height and position relative with the eccentric axial portion side of piston.At the cylinder block, be provided with oil collection part than the front end of the eccentric axial portion upper end portion of the bent axle position above more.
According to this structure, make lubricant oil and oil collection part collision from the ejection of the eccentric axial portion upper end portion of bent axle, import to the cylinder block the notch part side and above piston fuel feeding the time, can be from the lubricant oil bleed hole to the back side of piston portion fuel feeding.Consequently, when can improve in the sealing of cylinder block and piston, the cooling action that also improves piston.The reduction of the compression efficiency the when lubrication of each slide part in the time of therefore can be to the running up of compressor and cooling action and low-speed running suppresses, thereby guarantees the reliability of compressor.
Description of drawings
Fig. 1 is the longitudinal section of the hermetic type compressor of embodiments of the present invention 1.
The longitudinal section that major component when Fig. 2 is the low-speed running of hermetic type compressor shown in Figure 1 is amplified.
The longitudinal section that major component when Fig. 3 is running up of hermetic type compressor shown in Figure 1 is amplified.
Fig. 4 is the enlarged view of eccentric axial portion of the bent axle of hermetic type compressor shown in Figure 1.
The longitudinal section that major component when Fig. 5 is the low-speed running of hermetic type compressor of embodiments of the present invention 2 is amplified.
The longitudinal section that major component when Fig. 6 is running up of hermetic type compressor shown in Figure 5 is amplified.
Fig. 7 is the stereogram of the oil collection plate of hermetic type compressor shown in Figure 5.
Fig. 8 is the longitudinal section of the hermetic type compressor of prior art.
Fig. 9 is the longitudinal section that the major component of hermetic type compressor shown in Figure 8 is amplified.
Embodiment
Below to the mode of execution of hermetic type compressor of the present invention, describe with reference to accompanying drawing.In addition, the present invention has more than and is limited to following mode of execution.
(mode of execution 1)
Fig. 1 is the longitudinal section of the hermetic type compressor of embodiments of the present invention 1.Fig. 2 and Fig. 3 are respectively the low-speed running of this hermetic type compressor and major component is amplified when running up longitudinal section.Fig. 4 is the enlarged view of eccentric axial portion of the bent axle of this hermetic type compressor.This hermetic type compressor has seal container 101, be housed in the motor drive mechanism with stator 103 and rotor 104 in the seal container 101 and be housed in compressing mechanism 106 in the seal container 101.
That is, contain the refrigeration agent that does not have demonstration among motor drive mechanism 105, compressing mechanism 106, lubricant oil 107 and the figure in the space 102 in the seal container of seal container 101 inside.Motor drive mechanism 105 is made of stator 103 and the rotor 104 that is built-in with the permanent magnet (not shown).Compressing mechanism 106 is driven by motor drive mechanism 105.Lubricant oil 107 is stored in the bottom in the seal container 101.Motor drive mechanism 105 drives with a plurality of operating frequencys that comprise less than the frequency of industrial power frequency by inverter driving dynamic control device (not shown).That the refrigeration agent in the seal container in the space 102 uses is representative hydrocarbon refrigerant R600a (isobutane) in the low natural refrigeration agent of global warming coefficient.
The block 115 that constitutes cylinder block 116 also has the main bearing portion 118 of the main shaft part 109 that supports bent axle 108 when having columnar pressing chamber 117.That is, cylinder block 116 has pressing chamber 117 in the mode supports main shaft portion 109 that can freely rotate.Piston 119 is can reciprocating mode being housed in pressing chamber 117.That is, piston 119 is inserted in cylinder block 116 with the state that can freely reciprocatingly slide.Joint 120 is connected eccentric axial portion 110 with piston 119.Particularly, piston 119 is linked together by the eccentric axial portion 110 of wrist pin 130 with bent axle 108 by joint 120.
And then, be provided with in order to allow the notch part 126 of the semicircular arc that wrist pin 130 inserts at the upper wall of the pressing chamber 117 of cylinder block 116.The radius of curvature of notch part 126 is bigger than the radius of curvature of piston 119.
The eccentric axial portion 110 of bent axle 108 is formed on relative eccentric place with the axle center of main shaft part 109, and rotor 104 is pressed into and is fixed on main shaft part 109.Be that main shaft part 109 combines with the rotor 104 of motor drive mechanism 105.
The 108a of fuel feeding portion that forms at bent axle 108 is made up of heeling pump 111 and viscosity pump 112.One end of the heeling pump 111 that forms in the bottom of main shaft part 109 is at lubricant oil 107 split sheds.Viscosity pump 112 is formed on the surface of bent axle 108, and its lower end is communicated with heeling pump 111, and spiral extension axially.
Be formed with attachment hole 113 in the upper end of eccentric axial portion 110.One end of attachment hole 113 is communicated with the upper end of viscosity pump 112, and the other end is space 102 split sheds in the seal container up of the upper end portion 128 of eccentric axial portion 110.That is, first end of the 108a of fuel feeding portion is in the lower openings of main shaft part 109, and second end is communicated with attachment hole 113.In the part that is provided with attachment hole 113 of eccentric axial portion 110, be formed with from attachment hole 113 and extend to the radial direction of eccentric axial portion 110, connect outer circumferential face and the lubricant oil bleed hole 114 of opening in addition.Lubricant oil bleed hole 114 is as the upper/lower positions opening: in the time of near piston 119 arrives lower dead centres, eccentric axial portion 110 sides of piston 119, back side portion 190 is in relative height and position with lubricant oil bleed hole 114.For example, the top of lubricant oil bleed hole 114 and the back side portion 190 that is positioned at piston 119, notch part 126 position nearby is relative.
In addition, the height and position of the upper end 128 of the eccentric axial portion 110 of bent axle 108, in the projection plane of the wall thickness L that is set at notch part 126 (hereinafter referred to as wall thickness face L), wherein, notch part 126 is arranged on cylinder block 116 tops, is semicircular arc.That is, the upper end 128 of eccentric axial portion 110, top low than the part of the notch part 126 that is formed with cylinder block 116, and be positioned at top 129 more top of piston 119.
Working method about the hermetic type compressor of above such structure is described.The rotor 104 of motor drive mechanism 105 rotates bent axle 108.Be accompanied by this and rotate, rotatablely moving of eccentric axial portion 110 passed to piston 119 by joint 120 and wrist pin 130.So, piston 119 to-and-fro motion in pressing chamber 117.Thus, be inhaled in the pressing chamber 117, after being compressed, be ejected into refrigeration system more here from the refrigerant gas of refrigeration system (not shown) space 102 in the seal container.Then repeat this circulation.
Because the rotation of bent axle 108, the lubricant oil 107 in the heeling pump 111 is taken out upward by centrifugal force, supplies with each slide part by viscosity pump 112.Like this, the lubricated limit of carrying out each slide part, lubricant oil 107 limits is drawn into the attachment hole 113 that is arranged on eccentric axial portion 110.
Be pulled into the lubricant oil 107 of attachment hole 113, spray upward from the upper end portion 128 of eccentric axial portion 110.In addition, the part of the lubricant oil 107 of attachment hole 113 is emitted (distribution) from lubricant oil bleed hole 114 along circumferencial direction.
At this moment fuel delivery, the centrifugal force that produces at heeling pump 111 places according to the rotation of following bent axle 108 changes.When the little low-speed running of centrifugal force, fuel delivery tails off as shown in Figure 2, and when running up, the fuel feeding quantitative change is many as shown in Figure 3.On the other hand, when low-speed running,, be the easy situation of leaking of refrigeration agent because the Sliding velocity of piston 119 is slow.Therefore for sealing between piston 119 and cylinder block 116, just need be when running up more fuel delivery.
In the present embodiment, when low-speed running, shown in the arrow of Fig. 2, spray along circumferencial direction via the upper end portion 128 of attachment hole 113 from eccentric axial portion 110, the lubricant oil 107 that disperses, since self surface tension effects and attached to eccentric axial portion 110 the surface and meanwhile owing to centrifugal force disperses.
Here, the upper end 128 of eccentric shaft 110 is positioned at top 129 more top of piston 119 as described above, and is formed in the relative position with the wall thickness face L of notch part 126, and notch part 126 is arranged on cylinder block 116, is semicircular arc.Therefore the lubricant oil 107 that disperses to substantially horizontal bumps against the wall of notch part 126 easily.The lubricant oil 107 that collides with the inner face of notch part 126 is along wall 129 fuel feeding above piston 119.The inner face of the notch part 126 of cylinder block 116 works as oil collection part like this.That is,, be provided with inner face as the notch part 126 of oil collection part at cylinder block 116, its be positioned at bent axle 108 eccentric axial portion 110 upper end 128 more the top.In addition, do not collide and the lubricant oil 107 that falls to gravitational direction 129 DFF Direct Fuel Feeds above piston 119 with notch part 126.
And then the part of the lubricant oil 107 in the attachment hole 113 is dispersed to substantially horizontal from the lubricant oil bleed hole 114 that is arranged on eccentric axial portion 110 simultaneously, collides with the back side portion 190 of piston 119.Then, the lubricant oil 107 that rebounds is supplied between piston 119 and the cylinder block 116 complementaryly, thereby guarantees the sealing between piston 119 and the pressing chamber 117 (cylinder block 116).
Therefore, even if using and freon (flon, the carbon orgon compound) the class refrigeration agent is compared under the situation of big hydrocarbon refrigerant, the external diameter of piston 119 also can be guaranteed sealing between pressing chamber 117 and the piston 119 by lubricant oil 107, make the leakage of refrigeration agent reduce, thereby suppress the reduction of compression efficiency.And then owing to can between piston 119 and cylinder block 116, supply with more lubricating oil 107, thereby can improve reliability.
In addition, when running up, because the Sliding velocity of piston 119 is fast, so refrigeration agent relatively is not easy to leak.Therefore only still less fuel delivery can satisfy the sealing between piston 119 and the pressing chamber 117 (cylinder block 116) when needing than low-speed running.In addition, pressing chamber 117 temperature inside that being accompanied by runs up causes rise, and the temperature of piston 119 also has the tendency of rising.
As shown in Figure 3, the ejection state of comparing lubricant oil 107 during with the low speed of Fig. 2 is different when running up.Be that lubricant oil 107 disperses along circumferencial direction and to the distant place via the upper end portion 128 and the lubricant oil bleed hole 114 of attachment hole 113 from eccentric axial portion 110.
Promptly, lubricant oil 107 from upper end portion 128 ejection of eccentric axial portion 110, because the cause that big, the fuel delivery of centrifugal force is many, the surface tension traction that is produced by the upper end portion 128 in eccentric axial portion 110 is lived, but towards the top of substantially horizontal, to the inner face radiation of seal container 101.
So the lubricant oil 107 of ejection bumps against the inside top surface of seal container 101, in the process of the bottom of getting back to seal container 101 along its inner face, to cool off, the temperature that can suppress each slide part rises.
On the other hand, from the lubricant oil 107 of lubricant oil bleed hole 114 along continuous straight runs ejection, bump against from the back side portion 190 of the piston 119 of cylinder block 116 turnover, thereby piston 119 grades are cooled off.In addition, the part of the lubricant oil 107 that rebounds between piston 119 and the cylinder block 116, is guaranteed the sealing between piston 119 and the pressing chamber 117 (and cylinder block 116) by complementary ground fuel feeding.
Therefore, when no matter when the low-speed running of compressor, still running up, can both can improve the reliability of compressor stably to each slide part fuel feeding of compressing mechanism 106.In addition, fuel feeding can be guaranteed the sealing between piston 119 and the pressing chamber 117 (cylinder block 116) in this way, can guarantee both sealings and reduces the leakage of refrigeration agent, can suppress the reduction of compression efficiency.
In addition shown in the image pattern 4 like this, preferably the front outer 138 to the upper end 128 of eccentric axial portion 110 carries out following chamfering (fillet) processing of 0.3mm by taper (taper, tapering).In addition preferably to the edge of opening 148 (bight) of attachment hole 113 so that its mode that is actually the right angle process.
Carried out chamfer machining by front end like this to eccentric axial portion 110, and/or the edge of opening 148 of attachment hole 113 is processed in the mode that is the right angle, the situation that forms the surface of the concavo-convex things such as (flash, overlaps) that do not have burr is preferred.
As mentioned above, during low-speed running, from attachment hole 113 along the circumferential direction spray the lubricant oil that disperses 107 since the surface tension effects of self attached to the surface of eccentric axial portion 110 and owing to centrifugal force disperses.At this moment, if the front outer 138 of eccentric axial portion 110 has been carried out chamfer machining, then lubricant oil 107 is attached to this chamfer machining face.Lubricant oil 107 will disperse while falling along circumferencial direction to substantially horizontal or gravitational direction because of capillary effect then.
When making the upper-end surface of eccentric axial portion 110 become level and smooth like this, just can guarantee the adhesive quality that the surface tension of the lubricant oil 107 crossed along eccentric axial portion 110 upper ends 128 surface flows is brought, can prevent the fuel feeding obstacle that the concavo-convex thing of burr etc. causes.Therefore, the ejection of the lubricant oil 107 in the time of can making the low-speed running of bent axle 108 is stable, can guarantee the collision amount to the wall thickness face L of the notch part 126 of lubricant oil 107.That is in the time of, can carrying out low-speed running effectively from the upper end portion 128 of eccentric axial portion 110 to the fuel feeding of the notch part 126 of cylinder block 116.Can guarantee above piston 119 129 fuel delivery thus, the reliability in the time that low-speed running can being improved.
In addition when running up, because in fact the edge of opening 148 of attachment hole 113 forms the right angle, lubricant oil 107 is not lived by the surface tension traction that the upper end portion 128 in eccentric axial portion 110 produces, but towards the top of substantially horizontal, to the inner face radiation of seal container 101.Promptly, make lubricant oil 107 capillary influence when the inner face of seal container 101 disperses, that produce in the upper end portion 128 of eccentric axial portion 110 (to adhering to of surface etc.) when being not easy to be subjected to running up, can be lubricated the ejection (disperse) of oil 107 effectively to the inner face of seal container 101 from the upper end portion 128 of eccentric axial portion 110.Can improve the cooling effect of the lubricant oil 107 of the effect of dispersing that is accompanied by lubricant oil 107 thus, the reliability when running up.
(mode of execution 2)
The longitudinal section that major component when Fig. 5 is the low-speed running of hermetic type compressor of embodiments of the present invention 2 is amplified.The longitudinal section that major component when Fig. 6 is running up of this hermetic type compressor is amplified.Fig. 7 is the stereogram of the oil collection plate of this hermetic type compressor.In addition, give identical symbol, mainly the content different with mode of execution 1 before described for present embodiment and mode of execution 1 identical structure member.
The structure that present embodiment is different with mode of execution 1 before is on the top of cylinder block 116, to be provided with the oil collection plate 150 as oil collection part.Oil collection plate 150 is illustrated in figure 7 as from the extended upward shape of cylinder block 116, is fixed on cylinder block 116 with screw 151 grades.And this extended size of oil collection plate 150, the mode that forms the interval of regulation with the top inner face with seal container 101 is set.That is, cylinder block 116 be provided with as the upper end 128 of the eccentric axial portion 110 that is positioned at bent axle 108 more above the oil collection plate 150 of oil collection part.
Therefore, the turning crankshaft 108 that is accompanied by motor drive mechanism 105 also rotates, and lubricant oil 107 (flows) towards the top from the upper end portion 128 of eccentric axial portion 110 via attachment hole 113 equally with mode of execution 1.Then lubricant oil 107 sprays along circumferencial direction from the upper end portion 128 of attachment hole 113 via eccentric axial portion 110, and sprays from lubricant oil bleed hole 114 along circumferencial direction.At this moment fuel delivery is the same with mode of execution 1, and is less when the less low-speed running of centrifugal force as shown in Figure 5, as shown in Figure 6 centrifugal force bigger run up the time more.
But when low-speed running, collide with oil collection plate 150 from the lubricant oil 107 of upper end portion 128 ejection of eccentric axial portion 110,129 flow down above piston 119.In addition from the also ejection above piston 119 of lubricant oil 107 of lubricant oil bleed hole 114.Therefore, can guarantee sealing between piston 119 and the cylinder block 116 by the fuel delivery of abundance.Therefore the same with mode of execution 1, can suppress the refrigeration agent reduction of the compression efficiency the during low-speed running of leakage easily, can guarantee the reliability of compressor.
In addition when running up, collide with the inside top surface of seal container 101 from the lubricant oil 107 of upper end portion 128 ejections of eccentric axial portion 110, from lubricant oil bleed hole 114 also along circumferencial direction ejection lubricant oil 107.Therefore, the same with mode of execution 1, the temperature that can suppress each slide part by the lubricant oil 107 with the inside top surface collision rises.Can guarantee the sealing between piston 119 and the pressing chamber 117 (cylinder block 116) by from lubricant oil 107 cooling pistons 119 of lubricant oil bleed hole 114 etc. in addition.
As mentioned above, present embodiment is the same with mode of execution 1, no matter when the low-speed running of compressor or when running up, can both be stably carries out fuel feeding to each slide part of compressing mechanism 106, can improve the reliability of compressor.In addition,, can guarantee the sealing between piston 119 and the pressing chamber 117 (cylinder block 116), can guarantee both sealings and reduce the leakage of refrigeration agent, can suppress the reduction of compression efficiency by such fuel feeding.
Present embodiment is and mode of execution 1 structure different, that be provided with oil collection plate 150 in addition.Therefore be applicable to that the volume that is accompanied by pressing chamber 117 enlarges, is difficult to guarantee the structure of wall thickness of the notch part 126 of cylinder block 116.
In addition in the present embodiment, also preferably the front outer 138 of the upper end 128 of eccentric axial portion 110 is carried out chamfer machining below the 0.3mm by taper.The edge of opening 148 (bight) of preferred in addition attachment hole 113 by so that its mode that is actually the right angle process.Realize the effect same thus with mode of execution 1.
The present invention is the compressor of revolution various type, can be widely used in household electric refrigerator that cooling cycle system is controlled from low performance to high performance scope or the machine that possesses the cooling cycle system device as vending machine, air-conditioning etc.
Claims (6)
1. hermetic type compressor is characterized in that possessing:
Seal container;
Be housed in the seal container and have the motor drive mechanism of stator and rotor; With
Be housed in the compressing mechanism in the seal container,
Described compressing mechanism possesses:
Main shaft part; Bent axle, this bent axle is made of the eccentric axial portion of the top that is arranged on described main shaft part, upper end in described eccentric axial portion is formed with attachment hole, be formed with the lubricant oil bleed hole of perforation to the radial direction of described eccentric axial portion from described attachment hole, first end is in the lower openings of described main shaft part, and second end has the fuel feeding portion that is communicated with described attachment hole;
The cylinder block, it supports described main shaft part and has pressing chamber in the mode that can freely rotate;
Piston, it is housed in the described pressing chamber in the mode that can move reciprocatingly; With
Joint, it connects described eccentric axial portion and described piston,
The described main shaft part of described bent axle combines with the described rotor of described motor drive mechanism,
Be provided with the notch part of semicircle arcuation at the upper wall of the described pressing chamber of described cylinder block,
Described lubricant oil bleed hole is arranged on the relative height and position of described eccentric axial portion side with described piston,
Be provided with at described cylinder block the described eccentric axial portion upper end that is positioned at described bent axle more above oil collection part.
2. hermetic type compressor as claimed in claim 1 is characterized in that:
The front end of the upper end portion of described eccentric axial portion is top lower than the part that is formed with described notch part of described cylinder block, and is positioned at the top top of described piston,
Described oil collection part is the inner face of the described notch part of described cylinder block.
3. hermetic type compressor as claimed in claim 1 is characterized in that:
Described oil collection part is the oil collection plate that is provided with on the top of described cylinder block.
4. hermetic type compressor as claimed in claim 3 is characterized in that:
Described oil collection plate has along the shape of the semicircle arcuation of described notch part.
5. hermetic type compressor as claimed in claim 1 is characterized in that:
The front outer of the described upper end of described eccentric axial portion has been implemented chamfer machining.
6. hermetic type compressor as claimed in claim 1 is characterized in that:
Opening periphery at the described attachment hole of described eccentric axial portion setting forms the right angle.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009233310A JP5347887B2 (en) | 2009-10-07 | 2009-10-07 | Hermetic compressor |
| JP2009-233310 | 2009-10-07 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201818470U true CN201818470U (en) | 2011-05-04 |
Family
ID=43916427
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010205896728U Expired - Lifetime CN201818470U (en) | 2009-10-07 | 2010-10-08 | Closed type compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP5347887B2 (en) |
| CN (1) | CN201818470U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112639061A (en) * | 2018-07-20 | 2021-04-09 | 松下电器制冷装置新加坡 | Hermetic refrigeration compressor and freezing/refrigerating apparatus using the same |
| CN113187697A (en) * | 2021-06-07 | 2021-07-30 | 珠海格力电器股份有限公司 | Connecting rod assembly, piston type compression mechanism and refrigerator |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111946589B (en) * | 2020-09-18 | 2024-08-30 | 浙江麦迪制冷科技股份有限公司 | Direct current compressor |
| CN112523996B (en) * | 2020-12-05 | 2022-06-21 | 江西泛宇压缩机科技有限公司 | Crankshaft of compressor |
| CN117846929B (en) * | 2024-03-08 | 2024-05-14 | 浙江安吉华意科技有限公司 | Transmission assembly with crank case and compressor |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6385270A (en) * | 1986-09-26 | 1988-04-15 | Matsushita Refrig Co | Motor-driven compressor |
| JP2002070742A (en) * | 2000-08-30 | 2002-03-08 | Sanyo Electric Co Ltd | Refrigerant compressor |
| JP2002081378A (en) * | 2000-09-06 | 2002-03-22 | Sanyo Electric Co Ltd | Cooling medium compressor |
| JP2003065236A (en) * | 2001-08-28 | 2003-03-05 | Matsushita Refrig Co Ltd | Hermetic electric compressor |
| JP2005146856A (en) * | 2003-11-11 | 2005-06-09 | Hitachi Home & Life Solutions Inc | Reciprocating compressor |
-
2009
- 2009-10-07 JP JP2009233310A patent/JP5347887B2/en active Active
-
2010
- 2010-10-08 CN CN2010205896728U patent/CN201818470U/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112639061A (en) * | 2018-07-20 | 2021-04-09 | 松下电器制冷装置新加坡 | Hermetic refrigeration compressor and freezing/refrigerating apparatus using the same |
| CN112639061B (en) * | 2018-07-20 | 2022-10-28 | 松下电器制冷装置新加坡 | Hermetic refrigeration compressor and refrigerator-freezer using same |
| CN113187697A (en) * | 2021-06-07 | 2021-07-30 | 珠海格力电器股份有限公司 | Connecting rod assembly, piston type compression mechanism and refrigerator |
Also Published As
| Publication number | Publication date |
|---|---|
| JP5347887B2 (en) | 2013-11-20 |
| JP2011080418A (en) | 2011-04-21 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
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. |
|
| CX01 | Expiry of patent term | ||
| CX01 | Expiry of patent term |
Granted publication date: 20110504 |