CN107795459A - Compressor and the refrigerator for possessing the compressor - Google Patents
Compressor and the refrigerator for possessing the compressor Download PDFInfo
- Publication number
- CN107795459A CN107795459A CN201710737256.4A CN201710737256A CN107795459A CN 107795459 A CN107795459 A CN 107795459A CN 201710737256 A CN201710737256 A CN 201710737256A CN 107795459 A CN107795459 A CN 107795459A
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- Prior art keywords
- mentioned
- compressor
- bent axle
- piston
- cylinder barrel
- Prior art date
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Links
- 238000007906 compression Methods 0.000 claims abstract description 34
- 230000006835 compression Effects 0.000 claims abstract description 33
- 230000005520 electrodynamics Effects 0.000 claims abstract description 20
- 239000003507 refrigerant Substances 0.000 claims abstract description 10
- 238000003860 storage Methods 0.000 claims description 4
- 239000000446 fuel Substances 0.000 abstract description 6
- 239000010687 lubricating oil Substances 0.000 description 11
- 238000003780 insertion Methods 0.000 description 6
- 230000037431 insertion Effects 0.000 description 6
- 238000004904 shortening Methods 0.000 description 5
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical group [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 238000000926 separation method Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 239000003921 oil Substances 0.000 description 3
- 101100313003 Rattus norvegicus Tanc1 gene Proteins 0.000 description 2
- 241000375392 Tana Species 0.000 description 2
- 238000004891 communication Methods 0.000 description 2
- 230000014509 gene expression Effects 0.000 description 2
- 235000015927 pasta Nutrition 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 239000011148 porous material Substances 0.000 description 2
- 230000003584 silencer Effects 0.000 description 2
- 230000000007 visual effect Effects 0.000 description 2
- 241000208340 Araliaceae Species 0.000 description 1
- 235000005035 Panax pseudoginseng ssp. pseudoginseng Nutrition 0.000 description 1
- 235000003140 Panax quinquefolius Nutrition 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 235000008434 ginseng Nutrition 0.000 description 1
- 230000005484 gravity 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
- 239000012212 insulator Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000013507 mapping Methods 0.000 description 1
- 235000012771 pancakes Nutrition 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 230000008719 thickening Effects 0.000 description 1
- 235000013311 vegetables Nutrition 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
- F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
Abstract
The present invention provides and both inhibits height dimension, is effectively improved the compressor of fuel delivery again and possesses the refrigerator of the compressor.Compression unit (20) possesses：Cylinder barrel (21)；Moved back and forth in cylinder barrel (21), so as to the piston (22) of compression refrigerant；The bent axle (23) of eccentric rotary is carried out using electrodynamic element (30)；The eccentric part (23p) of bent axle (23) and the connecting rod (25) of piston (22) can rotatably be linked；Piston (22) and the piston pin (29) of connecting rod (25) can rotatably be linked；And the journal bearing (26) of e axle supporting bent axle (23), in the upper end of the main shaft (23a) of bent axle (23), the thickness of radially projecting flange part (23b) is below 4mm.
Description
Technical field
The present invention relates to a kind of compressor and possesses the refrigerator of the compressor.
Background technology
The compressor of Reciprocatory rotates crankshaft eccentric with the power by using motor and makes reciprocating motion of the pistons
The mechanism of compression refrigerant.Moreover, in recent years, with the power saving (high efficiency) for seeking refrigerator, compressor is similarly
Seek high efficiency.Therefore, compressor can be more than low operating frequency to the commercial power frequency less than commercial power frequency
High-frequency wide region in operating.If the operation continuation long period that compressor is carried out with low operating frequency, this part
Time can save electric power, and therefore, it is particularly important to the power saving of refrigerator to make compressor low-speed running.But if make compression
Machine low-speed running, then there is a possibility that supply to the amount of the lubricating oil between cylinder barrel and piston reduces.Therefore, as even in
During low-speed running also can efficiency supply the technology of lubricating oil well, motion has patent document 1 etc..
Prior art literature
Patent document
Patent document 1：Japanese Unexamined Patent Publication 2015-206269 publications
The content of the invention
Invent problem to be solved
But in the technology that above-mentioned patent document 1 is recorded again, it is difficult to both suppressed the overall height dimension of compressor, and had
Improve fuel delivery in effect ground.
The present invention solves the problems, such as above-mentioned existing, it is therefore intended that, there is provided height dimension is both inhibited, is effectively improved again
The compressor of fuel delivery and the refrigerator for possessing the compressor.
For solving the scheme of problem
The present invention is compressor, is possessed：Compression unit；Drive the electrodynamic element of above-mentioned compression unit；And storage is above-mentioned
The container of compression unit and above-mentioned electrodynamic element, the compressor are characterised by that above-mentioned compression unit possesses：Cylinder barrel；Above-mentioned
Moved back and forth in cylinder barrel, so as to the piston of compression refrigerant；The bent axle of eccentric rotary is carried out using above-mentioned electrodynamic element；Energy
The bar of enough eccentric parts and above-mentioned piston for rotatably linking above-mentioned bent axle；And the bearing of the above-mentioned bent axle of support, in above-mentioned bent axle
The thickness of the radially projecting flange part in upper end of main shaft be below 4mm.
Invention effect
Height dimension is both inhibited in accordance with the invention it is possible to provide, is effectively improved the compressor and tool of fuel delivery again
The refrigerator of the standby compressor.
Brief description of the drawings
Fig. 1 is the longitudinal section for the compressor for representing present embodiment.
Fig. 2 is the sectional elevation for the compressor for representing present embodiment.
Fig. 3 is the explanation of the position dimension at each angle of inclination based on gap when representing to obtain the interference rate of compressor
Figure.
Fig. 4 is the chart for representing interference rate and COP relation.
Fig. 5 is the chart for the relation for representing interference rate and main axis length/distance between tie rods.
Fig. 6 expressions are equipped with the schematic cross sectional view of the refrigerator of the compressor of present embodiment, and (a) is to be configured at compressor
The structure of bottom, (b) are the structures that compressor is configured to top.
In figure：
3-closed container, 9-disc spring, 10-rubber base, 20-compression unit, 21-cylinder barrel, 22-piston, 23-bent
Axle, 23a-main shaft, 23b-flange part, 23p-eccentric part, 24-framework, 24a-base, 24b-through hole, 24c-recessed
Portion, 24d-extension, 25-connecting rod (bar), 25a-small end, 25a1-connecting hole, 25b-big end, 25b1-link
Hole, 26-journal bearing (bearing), 27-thrust bearing, 28-top cover, 29-piston pin, 30-electrodynamic element, 31-rotor,
32-stator, 100-compressor, A~E-angle of inclination, the height of H-small end, L-main axis length, P-distance between tie rods,
Q2-compressor room side, the opposite side of Q3-compressor room.
Embodiment
Hereinafter, referring to the drawings, the compressor 100 of embodiments of the present invention is illustrated.
Fig. 1 is the longitudinal section for the compressor for representing present embodiment.
As shown in figure 1, compressor 100 is that compression unit 20 and electrodynamic element 30 are configured in closed container 3 and formed
So-called reciprocating compressor.Compression unit 20 and electrodynamic element 30 are interior via multiple disc springs 9 (elastomeric element) in closed container 3
It is elastically supported.Closed container 3 is made up of the upper shell 3m of the profile of roughly upper half engagements such as welding and formed substantially
The lower house 3n of the profile of the latter half, internally there is the space of storage compression unit 20 and electrodynamic element 30.
Compression unit 20 is configured to, and possesses：Cylinder barrel 21；Moved back and forth in the cylinder barrel 21 and carry out the work of compression refrigerant
Plug 22；The bent axle 23 (crank axle) of eccentric rotary is carried out using electrodynamic element 30；Link the eccentric part 23p and piston 22 of bent axle 23
Connecting rod 25 (bar)；Support the journal bearing 26 (bearing) and thrust bearing 27 (bearing) of bent axle 23.
Cylinder barrel 21 is formed at the position in the outside of the central shaft O deviation radial directions than bent axle 23 (main shaft 23a).In addition, cylinder barrel
21 axial O1 is configured to the direction vertical with respect to the axial direction (central shaft O) of bent axle 23.In addition, cylinder barrel 21 axial O1 it is outer
The end of the week side of boss is provided with top cover 28, in the end of opposite side inserted with piston 22.So, by cylinder barrel 21, piston 22 and top
Lid 28 constitutes discharge chambe (cylinder barrel room) Q1.In addition, valve switching mechanism (not shown) is provided between cylinder barrel 21 and top cover 28, should
Valve switching mechanism possesses the inlet valve opened in absorption refrigeration agent and the discharge opened in the refrigerant that discharge have compressed
Valve.
Piston 22 links via piston pin 29 and the small end 25a (end of the side of piston 22) of connecting rod 25.That is, in piston
The recess 22b of the 22 small end 25a insertions formed with the connecting hole 22a penetrated in the vertical direction and for connecting rod 25.
Bent axle 23 is configured to possess main shaft 23a, to radially projecting flange part 23b and formed in main shaft 23a upper end
Eccentric part 23p in the position for the central shaft O for deviateing main shaft 23a.Main shaft 23a central shaft O is set as the rotation with eccentric part 23p
It is parallel to turn central shaft.In addition, the bottom of bent axle 23 is extended near lower house 3n.Eccentric part 23p is inclined relative to central shaft O
The heart rotates, so as to which piston 22 moves back and forth in cylinder barrel 21.
Main shaft 23a is in the cylindrical shape extended in vertical, and is rotatably supported by journal bearing 26.Separately
Outside, main shaft 23a central shaft O (axial direction) is configured to axially in parallel with journal bearing 26.
Flange part 23b turns into the structure for being also used as balance weight.Balance weight has the vibration reduced when compression unit 20 drives
Function.Therefore, by balance weight between main shaft 23a and eccentric part 23p, so as to reduce the height of compression unit 20
Size, it can aid in the miniaturization of compressor 100.
In addition, it is configured in the main shaft 23a of bent axle 23, from the lower surface of axial direction upward, formed with concave bore hole
23c, and there is hollow bulb in main shaft 23a.In addition, in bent axle 23 formed with from bore hole 23c upper end towards flange part 23b's
The upper communication hole 23d penetrated above.In addition, in the outer peripheral face of bent axle 23, until near flange part 23b, formed with spiral
Groove 23e.
In eccentric part 23p, from the upper surface of the axial direction bore hole 23f formed with concave shape downward.Bore hole 23f is apart
The depth of upper surface is formed as shorter than eccentric part 23p axial length.In addition, bore hole 23f is via intercommunicating pore 23g and helicla flute
23e upper end connection.
Main shaft 23a hollow bulb inserted with stationary shaft member 23h.Stationary shaft member 23h fixtures 23i is fixed as i.e.
Make also not rotate when bent axle 23 rotates.Stationary shaft member 23h outer peripheral face formed with fixing axle helicla flute 23j.Consolidated by this
Dead axle helicla flute 23j wall and bore hole 23c wall form spiral helicine oil passage, with by (the main shaft of bent axle 23
Wall caused by rotation 23a) moves, and due to the effect of viscosity, lubricating oil being drawn to wall, and in fixing axle helicla flute
Rise in 23j.
Framework 24 has the base 24a extended in generally horizontal directions, and cylinder barrel 21 is located at base 24a top.In addition,
The drum of (towards lower house 3n bottom surface) extension is formed below oriented vertical in the substantially central portion of framework 24
Journal bearing 26.In addition, framework 24 constitutes a part for cylinder barrel 21.
Connecting rod 25 (bar) has small end 25a and big end 25b (partially to link the part of piston 22 and bent axle 23
The end of center portion 23p sides).In small end 25a, insertion ground is formed with the circular company inserted for piston pin 29 in the vertical direction
Tie hole 25a1.In big end 25b, insertion ground is formed with the circular connecting hole for eccentric part 23p inserts in the vertical direction
25b1。
Small end 25a connecting hole 25a1 axial direction is configured to axially in parallel with piston pin 29.Big end 25b link
Hole 25b1 axial direction is configured to axially in parallel with eccentric part 23p.
Journal bearing 26 is made up of the main shaft 23a of e axle supporting bent axle 23 sliding bearing.In addition, journal bearing 26 has
The through hole 26b penetrated on above-below direction.In addition, the supports main shaft 23a of journal bearing 26 part.That is, journal bearing 26
Upper end 26a is located at flange part 23b substantially lower end, and the lower end 26c of journal bearing 26 is located at bore hole 23c short transverse substantially
Center.
Thrust bearing 27 be configured at rounded channel-shaped be formed at base 24a through hole 26b opening edge recess
24c.The thrust bearing 27 is made up of one group of track plates 27a, 27b, retainer 27c and rolling element 27d.The thrust bearing 27
It is configured between the flange part 23b of bent axle 23 and recess 24c.
Track plates 27a shapes, and be configured to connect with recess 24c bottom surface 24c1 in a ring positioned at downside.Positioned at upside
Track plates 27b shapes, and be configured to connect with flange part 23b lower surface 23b1 in a ring.
Piston pin 29 inserts the connecting hole 25a1 both sides of the connecting hole 22a and small end 25a into piston 22, so as to revolve
Turn ground and link piston 22 and connecting rod 25.In addition, the axial direction (diagram above-below direction) of piston pin 29 is configured to the company with piston 22
Tie the axially in parallel of hole 22a.
Emerge to flange part 23b, moisten by upper communication hole 23d in the lubricating oil (refrigerator oil) that bore hole 23c rises
Sliding thrust bearing 27.In addition, bent axle 23 helicla flute 23e rise lubricating oil to bent axle 23 (main shaft 23a) and journal bearing
It is lubricated between 26, and is flowed into by intercommunicating pore 23g to eccentric part 23p bore hole 23f, the periphery of connecting rod 25 is carried out
Lubrication.In addition, the lubricating oil that have lubricated the grade of thrust bearing 27 is configured to, the hole 24s (reference picture 2) through being formed from framework 24 is returned
Go back to the bottom of closed container 3.
Electrodynamic element 30 is configured to, and is configured at the downside (base 24a lower section) of framework 24, and includes rotor 31 and stator
32。
Rotor 31 possesses the rotor core that laminated electromagnetic steel plate forms and formed, and is fixed on the (master of bent axle 23 by press-in etc.
Axle 23a) bottom.In addition, rotor 31 is the radius R flat pattern bigger T1 than thickness (axial height).In addition, rotor 31
Thickness (axial height) T1 is set as the degree of the substantially half of the length (bearing length) of journal bearing 26.
Stator 32 is configured to, and is configured at the periphery of rotor 31, and possesses：By cylindric stator core and it is formed at the stator
The iron core 32a that multiple slots in the inner circumferential of core are formed；And it is wound in iron core 32a coil across insulator (not shown)
32b.In addition, in Fig. 1 vertical profile regards the visual field, iron core 32a is that the length L1 of radial direction is more flat than what thickness (axial height) T2 grew
Flat shape shape.In Fig. 1 vertical profile regards the visual field, coil 32b is also the length of the radial direction pancake longer than thickness (axial height)
Shape.In addition, iron core 32a thickness (axial height) T2 is configured to and the same degree of the thickness of rotor 31 (axial height) T1.
Therefore, in the case where making rotor 31 be formed as flat, the diameter of stator 32 is made also to extend and be formed as flat pattern, so as to
Enough torques obtained for rotating rotor 31.
Then, framework 24 provided with compression unit 20 and electrodynamic element 30 in closed container 3 via multiple disc springs 9,9 and
It is elastically supported.In addition, when compression unit 20 and electrodynamic element 30 to vibrate in the running, not with closed container 3
The mode of wall contact is designed as having preset defined clearance C L state.
Disc spring 9 located at form compression unit 20 a part the side of cylinder barrel 21 (compressor room side Q2, Fig. 1 left side) and
The side (compressor room opposite side Q3, Fig. 1 right side) opposite with the side of cylinder barrel 21.In addition, in the present embodiment, be configured to,
Disc spring 9 in each of discharge chambe side and the opposite side of discharge chambe, be respectively arranged on the direction orthogonal with Fig. 1 paper with front side and
Depth side, closed container 3 are supported (reference picture 2) by four disc springs 9 altogether.In addition, all disc springs 9 are respectively provided with identical shape
And spring performance.Therefore, by the way that disc spring 9 is set into single kind, in the case of can preventing the mixing of disc spring 9 that there is variety classes
Configuration error.But the radical of disc spring 9 is not limited to four or three or more than five.
In addition, framework 24 has the extension 24d that the outer circumferential side (radial outside) in cylinder barrel 21 extends.Extension 24d
Extend to than 32 outer the week side of boss of stator.In addition, in extension 24d lower surface formed with the chimeric top for being held in disc spring 9
Jut 24e.
In addition, framework 24 also has the stretching with degree extended with extension 24d in the side opposite with extension 24d
Portion 24f.Extension 24f is also extended to than 32 outer the week side of boss of stator.In addition, in extension 24f lower surface formed with chimeric
It is held in the jut 24g on the top of disc spring 9.
In the bottom surface of closed container 3, in the outer circumferential side of stator 32, formed with grand in a manner of prominent into closed container 3
The stage portion 3a risen.A part for lower house 3n bottom surface and the part closure of side, outer surface turn into concave shape, so as to
Constitute stage portion 3a.In addition, stage portion 3a is located at the position with the position correspondence of disc spring 9.In addition, in the upper of stage portion 3a
End face formed with chimeric keeps the jut 3b of the bottom of disc spring 9.Jut 3b is positioned at more top than the lower surface 31a of rotor 31
Side.In addition, the pasta 40 of lubricating oil is configured to be located at the lower surface than rotor 31 in a manner of lubricating oil will not impregnate rotor 31
31a is on the lower.In addition, the lower end of bent axle 23 (main shaft 23a) and stationary shaft member 23h lower end are positioned at than pasta 40 on the lower.
Fig. 2 is the sectional elevation for the compressor for representing present embodiment.In addition, in fig. 2, to the system in compressor 100
The flowing of cryogen illustrates.
As shown in Fig. 2 returned from the cooler 66 (reference picture 6) of refrigerator and the suction of closed container 3 is connected from insertion
The refrigerant that pipe 3e is imported compresses after being inhaled into from the suction inlet of absorbing silencer 41 (not shown) via the importing of the grade of top cover 28
Room Q1 (reference picture 1).In addition, in discharge chambe Q1 by the refrigerant that piston 22 have compressed by discharge room space (not shown), then
By exhaust silencer 42a, the 42b and pipe 3f being formed on framework 24, from discharge pipe 3g by condenser (not shown), decompression
Device (not shown) and be delivered to cooler 66 (reference picture 4).
In the compressor 100 so formed, compression unit 20 is configured with the top of framework 24, electricity is configured with bottom
Moving cell 30, framework 24 are elastically supported in closed container 3 via disc spring 9,9.In this case, center of gravity is located at the height of framework 24
Position (position with the upper end of disc spring 9,9 with degree) is spent, compression unit 20 and electrodynamic element 30 are included therefore, it is possible to reduce
The deflection angle in internal mechanism portion.In addition, the outer circumferential side by the way that the position of disc spring 9 to be configured to cylinder barrel 21, can be further effective
Ground suppresses the vibration in above-mentioned internal mechanism portion.Therefore, it is possible to suppress the vibration in internal mechanism portion, so as to reduce internal mechanism
Clearance C L (reference picture 1) of portion's (compression unit 20 and electrodynamic element 30) between closed container 3.As a result, it can reduce close
Container 3 is closed, the miniaturization of compressor 100 can be realized.
In addition, it is provided with the rubber base 10 (reference picture 1) of resilient support closed container 3 in each stage portion 3a bottom.The rubber
The plate 11 that rubber base 10 is fixed in the lower house 3n of closed container 3 supports.In addition, rubber base 10 is at vertical (above-below direction)
On be configured at the position overlapping with disc spring 9.Stage portion 3a is so formed, disc spring 9 is configured in stage portion 3a, so as to by disc spring
9 are arranged to not lubricated oil impregnated height, therefore, it is possible to prevent that disc spring 9, can in noise caused by lubricating oil internal vibration
Realize the calmnessization of compressor 100.In addition, the bottom by the way that rubber base 10 to be configured to stage portion 3a, can prevent rubber base
10 significantly protrude downwards from the lower house 3n of closed container 3, are uprised therefore, it is possible to suppress the height of compressor 100, can
Realize the miniaturization of compressor 100.
Here, to the height dimension overall for both suppressing compressor 100, the bent axle 23 of fuel delivery is effectively improved again
Structure illustrates.First, the various pieces of the structure member of compressor 100 are thinned by inventor etc., and repetition test is strong
Whether there is no problem on degree, is found after discussion, for flange part 23b, has the leeway being thinned.Further, it was found that pass through
Thickness at present for the flange part 23b of 7~9mm degree is made less than 4mm (being preferably more than 2mm below 3mm), can be effective
Ground increases the amount to the lubricating oil supplied between cylinder barrel 21 and piston 22.Hereinafter, its principle is described.
, also can be by the overall shifting of cylinder barrel 21 even if not reducing the sectional area of cylinder barrel 21 when reducing flange part 23b thickness
Move to relatively low position.That is, the basal surface position (Fig. 1 S) of thrust bearing 27 and the axis center position (figure of cylinder barrel 21 can be reduced
1 O1) distance.As a result, the upper end level of cylinder barrel 21 reduces, therefore it is accessible to from the bore hole 23f lubricating oil sputtered
The upper surface of piston 22.Especially, the compressor 100 of present embodiment uses inverse changing driving circuit, and rotating speed is controlled for example
800~4300rpm scope, even also ensuring that fuel delivery as 800pm during low-speed running, therefore it can realize reliable
Property and all high compressor of efficiency.Further, since cylinder barrel 21 can be integrally provided in relatively low position, therefore compressor 100
Overall height dimension also diminishes (below 130mm).Moreover, the distance by reducing cylinder barrel 21 and thrust bearing 27, can drop
Load caused by the low torque for putting on main shaft 23a, also there is the effect for the abrasion for suppressing main shaft 23a.
If here, bent axle 23 offset (main shaft 23a axis center position and eccentric part 23p axis center position away from
From) larger, then in order to keep intensity, produce the demand for thickening flange part 23b.But if the offset of bent axle 23 is located at 9mm
Hereinafter, then easily flange part 23b is thinned as described above.
Next, reference picture 3 to Fig. 5, is fought to the finish, the distance between tie rods P for determining compressor 100 and the scheme of main axis length L relation are entered
Row explanation.Fig. 3 is the explanation of the position dimension at each angle of inclination based on gap when representing to obtain the interference rate in compressor
Figure, Fig. 4 is the chart for representing interference rate and COP relation, and Fig. 5 is the relation for representing interference rate and main axis length/distance between tie rods
Chart.In addition, Fig. 3 is to schematically show the angle of inclination based on each gap for ease of understanding.
In addition, as one of COP (Coefficient Of Performance) principal element for determining compressor, energy
Enough enumerate interference rate.The interference rate can be obtained by following formula (1).In addition, in the explanation of following formula (1), by song
Axle is referred to as axle, and connecting rod is referred to as into bar, and cylinder barrel and journal bearing are referred to as into framework.In addition, it is base that α, β, γ, δ are (not shown)
In the angle of inclination of geometric tolerances, A, B, C, D, E are the angles of inclination based on gap.In addition, on α~δ, by what is used in real time
The footpath size of each part is documented in bracket.
Interference rate=(alpha+beta+γ+δ)/(A+B+C+D+E) ... (1)
α：Angle of inclination (the main shaft based on the depth of parallelism of bent axle- eccentric part)
β：Angle of inclination (the big end based on the depth of parallelism of bar- small end)
γ：Angle of inclination (the external diameter based on perpendicularity of piston- connecting hole)
δ：Angle of inclination (the cylinder barrel based on perpendicularity of framework- journal bearing)
A：Framework (journal bearing)-axle (main shaft)
B：Bent axle (eccentric part)-bar (big end)
C：Bar (small end)-piston pin
D：Piston pin-piston
E：Piston-framework (cylinder barrel)
α is the main shaft 23a and eccentric part 23p of bent axle 23 depth of parallelism, as one, by main shaft 23a diameter (external diameter)
18mm is set to, eccentric part 23p diameter (external diameter) is set to 15.9mm.β is the small end 25a and big end 25b of connecting rod 25
The depth of parallelism, as one, big end 25b connecting hole 25b1 diameter is set to 15.9mm, by small end 25a connecting hole
25a1 diameter is set to 9.5mm.γ is the external diameter of the cylindrical portions of piston 22 and hanging down for the connecting hole 22a for the insertion of piston pin 29
Straight degree, as one, 25.4mm is set to by external diameter, connecting hole 22a diameter (external diameter) is set into 9.5mm.δ is the cylinder of framework 24
The perpendicularity of the axial direction (diagram left and right directions) of cylinder 21 and the axial direction (diagram above-below direction) of journal bearing 26, will as one
The internal diameter of cylinder barrel 21 is set to 25.4mm, and the diameter (internal diameter) of journal bearing 26 is set into 18mm.
As shown in figure 3, A is due to the gap between the main shaft 23a of bent axle 23 and journal bearing 26, main shaft 23a is radially
Angle of inclination when bearing 26 is tilted.B is due between big end 25b and bent axle 23 the eccentric part 23p of connecting rod 25
Gap, angles of inclination of the eccentric part 23p when big end 25b is tilted.C is due to the small end 25a and piston of connecting rod 25
Gap between pin 29, angle of inclination of the piston pin 29 when small end 25a is tilted.D is due to piston pin 29 and piston 22
Connecting hole 22a between gap, angle of inclination of the piston pin 29 when connecting hole 22a is tilted.E is due to piston 22 and frame
Gap between the cylinder barrel 21 of frame 24, angle of inclination of the piston 22 when cylinder barrel 21 is tilted.
Then, as angle of inclination A, B, C, D, E according to Fig. 3, when obtaining tanA, tanB, tanC, tanD, tanE,
It can be represented with following formula (2)~(6).Further, since the unit of intermediate gap is micron, therefore formula (2)~(6) record
" × 1000 " are in order that unit is consistent with millimeter.
TanA=CLa/ (La × 1000) ... (2)
TanB=CLb/ (Lb × 1000) ... (3)
TanC=CLc/ (Lc × 1000) ... (4)
TanD=CLd/ (Ld × 1000) ... (5)
TanE=CLe/ (Le × 1000) ... (6)
In addition, CLa is in the axial end (lower end) of journal bearing 26, main shaft 23a and journal bearing 26 separate away from
From La is the sliding length for the main shaft 23a journal bearings 26 slided.CLb be big end 25b axial end (on
End), the distance of eccentric part 23p and big end 25b separation, Lb is the sliding length for the eccentric part 23p big end 25b slided.
CLc is that Lc is to supply piston pin in the distance of small end 25a axial end (lower end), piston pin 29 and small end 25a separation
The 29 small end 25a slided sliding length.CLd is in the end (upper end) in the direction orthogonal to the axial direction of piston 22, piston
The distance of 22 connecting hole 22a and piston pin 29 separation, Ld are the connecting hole 22a slided for piston pin 29 sliding lengths.CLe
For the axial end in piston 22, the distance of cylinder barrel 21 and the separation of piston 22, Le is the cunning of the cylinder barrel 21 slided for piston 22
Dynamic length.
When according to above-mentioned formula (2)~(6), when obtaining A~E, turning into following formula (7)~(11).
A=arctan (CLa/ (La × 1000) ... (7)
B=arctan (CLb/ (Lb × 1000) ... (8)
C=arctan (CLc/ (Lc × 1000) ... (9)
D=arctan (CLd/ (Ld × 1000) ... (10)
E=arctan (CLe/ (Le × 1000) ... (11)
Therefore, each angle of inclination A~E is represented if collecting, as formula (12) as shown below.
Arctan (each gap/(sliding length × 1000)) (12)
In addition, after being inquired into the interference rate and COP relation obtained by above-mentioned formula (1), it is thus identified that obtain as follows
Relation：As shown in figure 4, the more low then COP of interference rate is higher.It is thus identified that the relation according to Fig. 4, obtains interference rate,
So as to improve the COP of compressor 100.
Therefore, Fig. 5 is represented to the numeral beyond the angle of inclination A of the formula (1) related to the length of bent axle 23 is set into solid
The ratio (L/P) of definite value and main axis length L and distance between tie rods P (reference picture 1) when making main axis length L (reference picture 1) length change
The figure that repeatedly mapping system forms is carried out with the relation of interference rate.In addition, the main axis length L in present embodiment is as shown in figure 1, be
Refer to from the main shaft 23a of bent axle 23 upper end, in other words, from flange part 23b lower surface 23b1 to the lower end of journal bearing 26
Length.Distance between tie rods P is as shown in figure 1, refer to the rotation for linking the small end 25a of connecting rod 25 pivot c1 and big end 25b
Turn center c2 distance.Therefore, by shortening main axis length L, so as to which L/P (main axis length/distance between tie rods) diminishes, led by increasing
Shaft length L, L/P become big.
As shown in Figure 5, it is thus identified that, as L/P becomes big, interference rate uprises.In addition, it is thus identified that, L/P exists near 1.1
Flex point.I.e., it is thus identified that, in the case where L/P is less than 1.1, interference rate changes along straight line S1, in situations of the L/P more than 1.1
Under, interference rate changes along straight line S2.Therefore, in the case where L/P is less than 1.1, interference rate can be both reduced, shortens main shaft again
Length L.In addition, in the case where L/P is more than 1.1, interference rate uprises, and main axis length L is elongated.Therefore, by the way that L/P is set
For less than 1.1, so as to shorten bent axle 23, the miniaturization of compressor 100 can be realized, and ensure the performance of compressor 100, energy
Enough prevent from acting bad (can prevent bent axle 23 from locking).In addition, in the past, (make compressor 100 small due to shortening main axis length L
Type), bearing loading can become big, therefore, all the time not by active adoption.But, it is thus identified that, even if shortening main axis length
L, by the way that L/P is set as into less than 1.1, it can also allow the increase of the increased bearing loading with bearing loading, can be both
Ensure the performance as compressor 100, realize miniaturization again.
If in addition, in order to for the purpose of improving the performance of compressor 100, and by piston 22 and the mode of connection of connecting rod 25
Piston pin mode is changed to from ball-and-socket joint, then requires high dimensional accuracy.But when shortening main axis length L, bent axle 23
Angle of inclination becomes big, therefore, it is possible to relax the precision of geometric tolerances.In addition, shorten main axis length L, so as to the formation of bent axle 23
Narrow for the bore hole 23c of stationary shaft member 23h insertions space.Narrowed by the space, compared with the longer situation of bent axle, circle
The region of the thin-walled portion of tubular can also narrow, therefore, it is possible to which the rigidity of bent axle 23 is improved into the degree.Bent axle 23 can be suppressed
Deflection deformation, even if so as to shorten bent axle 23 minimize compressor 100, also ensure that the performance as compressor 100.
In addition, in the present embodiment, in compressor 100, (the ginseng when small end 25a axial height is set into H
According to Fig. 1), main axis length L is set to 3~5 times of height H, so as to relax the axial direction of the axial direction of piston pin 29 and main shaft 23a
The precision of the depth of parallelism of (central shaft O).Therefore, compressor 100 is minimized even if shortening bent axle 23, can also ensure that as pressure
The performance of contracting machine 100.
Fig. 6 expressions are equipped with the schematic cross sectional view of the refrigerator of the compressor of present embodiment, and (a) is to be configured at compressor
The structure of bottom, (b) are the structures that compressor is configured to top.
As shown in Fig. 6 (a), refrigerator 60A is that refrigerator main body 61 is divided into multiple receiving rooms 62,63,64,65 and formed.Example
Such as, receiving room 62 is refrigerating chamber, and receiving room 63 is top freezer compartment, and receiving room 64 is lower freezer compartment, and receiving room 65 is vegetables
Room.In addition, the position relationship of each receiving room 62,63,64,65 is not limited to Fig. 6 (a).Compressor 100 is configured at taking out for receiving room 65
The Machine Room of drawer 65a depth side lower part (bottom of the rear side of refrigerator main body 61).The refrigerant discharged from compressor 100
By condenser (not shown), the mechanism of decompressor (not shown) being arranged in refrigerator 60A, the heat in refrigerator is absorbed in cooler 66
Amount, and again return in compressor 100.
But if need to increase the volume of Machine Room, therefore be accommodated in using the compressor that build is high as at present
The drawer 65a of receiving room 65 capacity can diminish and (turn into shallower drawer).Therefore, by using applying present embodiment
The refrigerator 60A of compressor 100, the volume of Machine Room can be reduced, the height and position in the top plate face of Machine Room can be reduced, therefore
The case inner capacities of the depth side of receiving room 65 can be expanded.
In addition, as shown in Fig. 6 (b), refrigerator 60B compressor 100 is configured at depth upper lateral part (the refrigerator master of receiving room 62
The rear side of body 61 is topmost) Machine Room in.
But if using the compressor that build is big as at present, vibration caused by compressor is larger, therefore, passes
Being delivered to the vibration of refrigerator main body can also become big.Therefore, by using the refrigerator 60B for the compressor 100 for applying present embodiment,
By above-mentioned construction, vibration can be reduced, therefore, it is possible to suppress to be delivered to the vibration of refrigerator main body 61.In addition, pass through application
Small-sized compressor 100, it can also expand the case inner capacities of receiving room 62.
Additionally, this invention is not limited to above-mentioned embodiment, can carry out without departing from the spirit and scope of the invention
Various changes.For example, in the present embodiment, carried out in case of linking piston 22 with connecting rod 25 with piston pin 29
Explanation is enumerated, but is not limited to piston pin 29, ball-and-socket joint mode can also be used.
Claims (4)
1. a kind of compressor, possesses：Compression unit；Drive the electrodynamic element of above-mentioned compression unit；And the above-mentioned compression list of storage
The container of first and above-mentioned electrodynamic element,
Above-mentioned compressor is characterised by,
Above-mentioned compression unit possesses：Cylinder barrel；Moved back and forth in above-mentioned cylinder barrel, so as to the piston of compression refrigerant；Utilize
Above-mentioned electrodynamic element carries out the bent axle of eccentric rotary；The eccentric part of above-mentioned bent axle and the bar of above-mentioned piston can rotatably be linked；
And the bearing of the above-mentioned bent axle of support,
In the upper end of the main shaft of above-mentioned bent axle, the thickness of radially projecting flange part is below 4mm.
2. a kind of compressor, possesses：Compression unit；Drive the electrodynamic element of above-mentioned compression unit；And the above-mentioned compression list of storage
The container of first and above-mentioned electrodynamic element,
Above-mentioned compressor is characterised by,
Above-mentioned compression unit possesses：Cylinder barrel；Moved back and forth in above-mentioned cylinder barrel, so as to the piston of compression refrigerant；Utilize
Above-mentioned electrodynamic element carries out the bent axle of eccentric rotary；The eccentric part of above-mentioned bent axle and the bar of above-mentioned piston can rotatably be linked；
And the bearing of the above-mentioned bent axle of support,
The offset of above-mentioned bent axle is below 9mm, in the thickness of the radially projecting flange part in the upper end of the main shaft of above-mentioned bent axle
For below 4mm.
3. compressor according to claim 1 or 2, it is characterised in that
Above-mentioned compression unit possesses the framework of the above-mentioned bent axle of e axle supporting,
Above-mentioned cylinder barrel is configured with the upside of said frame, above-mentioned electrodynamic element is configured with the downside of said frame,
Said frame is supported in said vesse via elastomeric element,
Above-mentioned elastomeric element is located at the outer circumferential side of above-mentioned cylinder barrel.
4. a kind of refrigerator, it is characterised in that possess compressor according to any one of claims 1 to 3.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016168728A JP2018035727A (en) | 2016-08-31 | 2016-08-31 | Compressor and refrigerator with the same |
| JP2016-168728 | 2016-08-31 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN107795459A true CN107795459A (en) | 2018-03-13 |
Family
ID=61531621
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710737256.4A Pending CN107795459A (en) | 2016-08-31 | 2017-08-24 | Compressor and the refrigerator for possessing the compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2018035727A (en) |
| CN (1) | CN107795459A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111075687A (en) * | 2018-10-22 | 2020-04-28 | Lg电子株式会社 | Compressor including cylinder block corresponding to outer rotor type motor |
| CN114930023A (en) * | 2019-12-03 | 2022-08-19 | 松下电器制冷装置新加坡 | Hermetic refrigerant compressor and refrigerator-freezer using the same |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5846216A (en) * | 1981-08-03 | 1983-03-17 | アスペラ・エス・ピ−・エ− | Crankshaft for small-sized reciprocating engine |
| CN1896505A (en) * | 2005-07-13 | 2007-01-17 | 乐金电子(天津)电器有限公司 | Crank equalizing frame for closed compressor |
| CN204783538U (en) * | 2015-06-29 | 2015-11-18 | 安徽美芝制冷设备有限公司 | A reciprocating compressor that is used for reciprocating compressor's bent axle and has it |
| CN105518299A (en) * | 2013-09-03 | 2016-04-20 | 松下知识产权经营株式会社 | Sealed compressor and freezer device or refrigerator equipped with same |
-
2016
- 2016-08-31 JP JP2016168728A patent/JP2018035727A/en active Pending
-
2017
- 2017-08-24 CN CN201710737256.4A patent/CN107795459A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5846216A (en) * | 1981-08-03 | 1983-03-17 | アスペラ・エス・ピ−・エ− | Crankshaft for small-sized reciprocating engine |
| CN1896505A (en) * | 2005-07-13 | 2007-01-17 | 乐金电子(天津)电器有限公司 | Crank equalizing frame for closed compressor |
| CN105518299A (en) * | 2013-09-03 | 2016-04-20 | 松下知识产权经营株式会社 | Sealed compressor and freezer device or refrigerator equipped with same |
| CN204783538U (en) * | 2015-06-29 | 2015-11-18 | 安徽美芝制冷设备有限公司 | A reciprocating compressor that is used for reciprocating compressor's bent axle and has it |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111075687A (en) * | 2018-10-22 | 2020-04-28 | Lg电子株式会社 | Compressor including cylinder block corresponding to outer rotor type motor |
| CN111075687B (en) * | 2018-10-22 | 2022-02-11 | Lg电子株式会社 | Compressor including cylinder block corresponding to outer rotor type motor |
| US11536258B2 (en) | 2018-10-22 | 2022-12-27 | Lg Electronics Inc. | Compressor including cylinder block corresponding to outer rotor type motor |
| CN114930023A (en) * | 2019-12-03 | 2022-08-19 | 松下电器制冷装置新加坡 | Hermetic refrigerant compressor and refrigerator-freezer using the same |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2018035727A (en) | 2018-03-08 |
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Application publication date: 20180313 |