CN107131109A - Compressor and the refrigerator for possessing the compressor - Google Patents
Compressor and the refrigerator for possessing the compressor Download PDFInfo
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- CN107131109A CN107131109A CN201710025343.7A CN201710025343A CN107131109A CN 107131109 A CN107131109 A CN 107131109A CN 201710025343 A CN201710025343 A CN 201710025343A CN 107131109 A CN107131109 A CN 107131109A
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- Prior art keywords
- compressor
- mentioned
- piston
- bent axle
- addition
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- 238000007906 compression Methods 0.000 claims abstract description 28
- 230000006835 compression Effects 0.000 claims abstract description 27
- 230000005520 electrodynamics Effects 0.000 claims abstract description 16
- 239000003507 refrigerant Substances 0.000 claims abstract description 10
- 230000004323 axial length Effects 0.000 claims description 4
- 238000003780 insertion Methods 0.000 description 8
- 230000037431 insertion Effects 0.000 description 8
- 239000010687 lubricating oil Substances 0.000 description 8
- 238000004904 shortening Methods 0.000 description 6
- 238000000926 separation method Methods 0.000 description 5
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical group [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 4
- 238000010586 diagram Methods 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
- 230000000694 effects Effects 0.000 description 2
- 230000033001 locomotion Effects 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 239000003921 oil Substances 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
- 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
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000000916 dilatatory effect Effects 0.000 description 1
- 230000003292 diminished effect Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 230000002349 favourable effect 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
- 238000005057 refrigeration Methods 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 230000006641 stabilisation Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 230000002194 synthesizing effect 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
- 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
- F04B39/0005—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 adaptations of pistons
-
- 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
- F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Compressor (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
The present invention provides a kind of compressor that can be prevented action failure and can minimize and the refrigerator for possessing the compressor.Compression unit (20) possesses：Cylinder barrel (21)；By being moved back and forth and the piston (22) of compression refrigerant in cylinder barrel (21)；The bent axle (23) of eccentric rotary is carried out by electrodynamic element (30)；The eccentric part (23p) of bent axle (23) and the connecting rod (25) of piston (22) can rotatably be linked；The piston pin (29) of piston (22) and connecting rod (25) can rotatably be linked；And the journal bearing (26) of e axle supporting bent axle (23), when the spacing as the pivot of the small end (25a) of connection connecting rod (25) and the distance of the pivot of big end (25b) is set into P, L/P is less than 1.1.
Description
Technical field
The present invention relates to compressor and possesses the refrigerator of the compressor.
Background technology
Reciprocating-type compressor has following mechanism, i.e. so that the power of motor makes crank axle eccentric rotary and makes piston past
Multiple motion, so that compression refrigerant (with reference to patent document 1).
Prior art literature
Patent document
Patent document 1：Japanese Unexamined Patent Publication 2010-281299 publications
The content of the invention
Invent problem to be solved
However, for reciprocating-type compressor, in addition to circularity, cylindricity except each sliding part are important, perpendicularity with it is parallel
The morpheme of degree etc., which is intersected, also becomes important.But, in the compressor that patent document 1 is recorded, when in order to realize the small of compressor
Type and when shortening crank axle, the gradient of crank axle becomes big, so that the load for acting on crank axle becomes big, in form and position tolerance
In the case that precision is low, there is the locking of final crank axle and compressor the problem of can not be operating normally.
The present invention solves above-mentioned existing issue, and its object is to provide a kind of pressure that prevents action failure and can minimize
Contracting machine and the refrigerator for possessing the compressor.
Scheme for solving problem
The present invention is a kind of compressor, and it possesses：Compression unit；Drive the electrodynamic element of above-mentioned compression unit；And receive
Receive the container of above-mentioned compression unit and above-mentioned electrodynamic element, above-mentioned compressor is characterised by that above-mentioned compression unit possesses：Cylinder
Cylinder；By being moved back and forth and the piston of compression refrigerant in above-mentioned cylinder barrel；Bias is carried out by above-mentioned electrodynamic element
The bent axle of rotation；The eccentric part of above-mentioned bent axle and the bar of above-mentioned piston can rotatably be linked；And the axle of the above-mentioned bent axle of supporting
Hold, the axial length from the upper end of the main shaft of above-mentioned bent axle to the lower end of above-mentioned bearing is being set to L, above-mentioned bar will connected
When the distance of the pivot of one end and the pivot of the other end is set to P, L/P is less than 1.1.
The effect of invention
In accordance with the invention it is possible to provide a kind of compressor that prevents action failure and can minimize and possess the compressor
Refrigerator.
Brief description of the drawings
Fig. 1 is the longitudinal sectional view for the compressor for representing present embodiment.
Fig. 2 is the transverse sectional view for the compressor for representing present embodiment.
Fig. 3 is to illustrate when obtaining the interference rate of compressor saying for because of caused by the gap position dimension at each angle of inclination
Bright 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 is the schematic cross sectional view for representing to be equipped with the refrigerator of the compressor of present embodiment, and (a) is to configure compressor
Structure in bottom, (b) is the structure that compressor is configured to top.
Symbol description
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-frame, 24a-base portion, 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 sectional view 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 constituted
So-called reciprocating compressor.Compression unit 20 and electrodynamic element 30 are in closed container 3 via multiple disc springs 9 (elastomeric element)
And be elastically supported.Upper shell 3m and composition of the closed container 3 by welding etc. to the composition generally outline of half
Substantially descend the lower house 3n of the outline of half to be engaged, and internally have compression unit 20 and electrodynamic element 30 are carried out
The space of storage.
Compression unit 20 is configured to, and possesses：Cylinder barrel 21；By being moved back and forth and compression refrigerant in the cylinder barrel 21
Piston 22；The bent axle 23 (crank axle) of eccentric rotary is carried out by electrodynamic element 30；Link eccentric part 23p and the work of bent axle 23
The connecting rod 25 (bar) of plug 22；And the journal bearing 26 (bearing) and thrust bearing 27 (bearing) of support 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 orthogonal with the axial direction (central shaft O) of bent axle 23.In addition, the periphery of the axial O1 in cylinder barrel 21
The end of side is provided with top cover 28, opposite side end inserted with piston 22.So, cylinder barrel 21, piston 22 and top are passed through
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 opened when the refrigerant that have compressed is discharged
Drain valve.
Piston 22 links via piston pin 29 with the small end 25a (end of the side of piston 22) of connecting rod 25.That is, in piston
22 are formed with：The connecting hole 22a of insertion in the vertical direction；And the recess 22b of the small end 25a insertions for connecting rod 25.
Bent axle 23 is configured to, and possesses：Main shaft 23a；In main shaft 23a upper end, the flange part 23b diametrically protruded；With
And it is formed at the eccentric part 23p with main shaft 23a central shaft O eccentric positions.Main shaft 23a central shaft O is set as and bias
Portion 23p Pivot axle is parallel.In addition, the bottom of bent axle 23 extends to lower house 3n vicinity.Eccentric part 23p relative to
Central shaft O carries out eccentric rotary, so that piston 22 moves back and forth in cylinder barrel 21.
Main shaft 23a is in the cylinder extended in vertical, and is rotatably supported by journal bearing 26.In addition,
Main shaft 23a central shaft O (axial direction) is configured to axially in parallel with journal bearing 26.
Flange part 23b is the construction for also serving as counterweight.Counterweight has the function of reducing vibration when compression unit 20 drives.From
And, it is located at by making counterweight between main shaft 23a and eccentric part 23p, the height dimension of compression unit 20 can be reduced, can be favourable
In the miniaturization of compressor 100.
In addition, being configured in the main shaft 23a of bent axle 23, from axial lower surface upward, the bore hole of concave shape is formed
23c, and with hollow bulb in main shaft 23a.In addition, being formed with bent axle 23 from bore hole 23c upper end towards flange part 23b's
The upper communication hole 23d of insertion above.In addition, the outer peripheral face in bent axle 23 is formed with helicla flute 23e, until flange part 23b
Vicinity.
In eccentric part 23p, from axial upper surface downward, the bore hole 23f of concave shape is formed with.Bore hole 23f is apart
The axial length that the depth of upper surface is formed as than eccentric part 23p is short.In addition, bore hole 23f is via intercommunicating pore 23g and spiral
Groove 23e upper end connection.
Main shaft 23a hollow bulb inserted with stationary shaft member 23h.Stationary shaft member 23h is fixed by fixture 23i
Also not rotated when bent axle 23 rotates.Fixing axle helicla flute 23j is formed with stationary shaft member 23h outer peripheral face.By
Fixing axle helicla flute 23j wall and bore hole 23c wall form spiral helicine oil passage, with (main by bent axle 23
Axle 23a) rotation caused by wall movement, lubricating oil by quasi-viscous effect along wall it is dilatory to fixing axle spiral
Rise in groove 23j.
Frame 24 has the base portion 24a extended in generally horizontal directions, and cylinder barrel 21 is located at base portion 24a top.In addition,
The columnar footpath of (towards lower house 3n bottom surface) extension is formed below oriented vertical in the substantially central portion of frame 24
To bearing 26.In addition, frame 24 constitutes a part for cylinder barrel 21.
Connecting rod 25 (bar) is the part for linking piston 22 and bent axle 23, and it has small end 25a and big end 25b (eccentric
The end of portion 23p sides).In small end 25a, the circular link inserted for piston pin 29 is formed with to insertion in the vertical direction
Hole 25a1.In big end 25b, the circular connecting hole 25b1 for eccentric part 23p inserts is formed with to insertion in the vertical direction.
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 supports the main shaft 23a of bent axle 23 sliding bearing to constitute by axle.In addition, journal bearing 26 has
The through hole 26b of insertion 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 is configured at is formed as the recess of circular channel-shaped in base portion 24a through hole 26b opening edge
24c.The thrust bearing 27 includes one group of track plates 27a, 27b, retainer 27c and rotor 27d.The thrust bearing 27 is configured
Between the flange part 23b and recess 24c of bent axle 23.
Positioned at downside track plates 27a in a ring, and configured in the way of the bottom surface 24c1 with recess 24c connects.It is located at
The regulation plate 27b of upside in a ring, and is configured in the way of the lower surface 23b1 with flange part 23b connects.
Piston pin 29 can be turned by inserting the connecting hole 22a and small end 25a of piston 22 connecting hole 25a1 both sides
Link piston 22 and connecting rod 25 dynamicly.In addition, the axial direction (diagram above-below direction) of piston pin 29 is configured to the link with piston 22
Hole 22a's is axially in parallel.
To spray above flange part 23b after the lubricating oil (refrigerator oil) that bore hole 23c rises is by upper communication hole 23d
Go out, into lubrication thrust bearing 27.In addition, bent axle 23 helicla flute 23e rise lubricating oil to bent axle 23 (main shaft 23a) with
Be lubricated between journal bearing 26, and by intercommunicating pore 23g after, towards eccentric part 23p bore hole 23f flow into, Jin Errun
The periphery of sliding connecting rod 25.In addition, the lubricating oil that have lubricated the grade of thrust bearing 27 is configured to, via the hole formed in frame 24
24s (reference picture 2) and the bottom for returning to closed container 3.
Electrodynamic element 30 is configured at the downside (base portion 24a lower section) of frame 24, and the structure comprising rotor 31 and stator 32
Into.
Rotor 31 possesses the rotor core of laminated electromagnetic steel plate and constituted, and is fixed on bent axle 23 by press-in etc.
The bottom of (main shaft 23a).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 substantially half or so of the length (bearing length) of journal bearing 26.
Stator 32 is configured to possess：Iron core 32a, it is configured at the periphery of rotor 31, and including cylindric stator core
The multiple slots formed with the inner circumferential in the stator core；Coil 32b, it is wound in iron core via insulator (not shown)
32a.In addition, in Fig. 1 longitudinal profile observation, iron core 32a is the length L1 of radial direction than thickness (axial height) T2 length
Flat pattern.In Fig. 1 longitudinal profile observation, coil 32b is also that the length of radial direction is more flat than thickness (axial height) length
Flat shape shape.In addition, iron core 32a thickness (axial height) T2 is configured to thickness (axial height) T1 phases with rotor 31
Together.So as in the case where rotor 31 is formed as into flat, be formed as flat by the way that the diameter of stator 32 is also widened
Shape, so as to obtain the torque for rotating rotor 31.
So the frame 24 provided with compression unit 20 and electrodynamic element 30 in closed container 3 via multiple disc springs 9 by
Resilient support.In addition, Design of State compression unit 20 and electrodynamic element 30 to be preset with predetermined clearance C L so that
When generating vibration during operating, do not contacted with the internal face of closed container 3.
Disc spring 9 is located at the side of cylinder barrel 21 (compressor room side Q2, Fig. 1 left side) for the part for constituting compression unit 20 and cylinder
The opposite side (compressor room opposite side Q3, Fig. 1 right side) of 21 sides of cylinder.In addition, present embodiment is configured to, disc spring 9 is in compression
Room side and the opposite side of discharge chambe respectively located at the direction orthogonal with Fig. 1 paper with front side and depth side, closed container 3 by
Four disc springs 9 are supported (reference picture 2) altogether.In addition, all disc springs 9 are respectively provided with identical shape and spring performance.So as to lead to
Crossing makes disc spring 9 be single kind, can prevent the configuration error in the case of different types of disc spring 9 is mixed.But, disk
The radical of spring 9 is not limited to four, can be three, or more than five.
In addition, frame 24 has the extension 24d extended to than the outer the week side of boss (radial outside) of cylinder barrel 21.The extension
24d is extended to than the outer the week side of boss of stator 32.In addition, the lower surface in extension 24d is formed with the chimeric top for being held in disc spring 9
Jut 24e.
In addition, frame 24 also has the extension extended with extension 24d with degree in extension 24d opposite side
24f.Extension 24f is also extended to than the outer the week side of boss of stator 32.In addition, the lower surface in extension 24f is formed with chimeric guarantor
It is held in the jut 24g on the top of disc spring 9.
In the bottom surface of closed container 3, it is formed with the outer circumferential side of stator 32 grand in prominent into closed container 3 mode
The order difference part 3a risen.Order difference part 3a is closed by a part for lower house 3n bottom surface and a part for side, and outside is formed
Concave shape and constitute.In addition, order difference part 3a is located at position corresponding with the position of disc spring 9.In addition, in order difference part 3a upper end
Face is formed with the jut 3b for the bottom for keeping disc spring 9 chimericly.Jut 3b is located at more top than the lower surface 31a of rotor 31
Side.In addition, the pasta 40 of lubricating oil is configured in the way of lubricating oil does not soak rotor 31, positioned at the lower surface than 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 located at than pasta 40 on the lower.
Fig. 2 is the transverse sectional view for the compressor for representing present embodiment.In addition, in fig. 2, in compressor 100
The flowing of refrigerant is illustrated.
As shown in Fig. 2 from the suction (not shown) of the suction inlet of absorbing silencer 41 from the cooler 66 (reference picture 6) of refrigerator
After the refrigerant that the suction line 3e for returning and being connected from insertion closed container 3 is imported, it is imported into pressure via the grade of top cover 28
Contracting room Q1 (reference picture 1).In addition, the refrigerant that have compressed by piston 22 in discharge chambe Q1 is by discharging room space (not shown)
Afterwards, by exhaust silencer 42a, 42b and pipe 3f for being formed in frame 24, from discharge pipe 3g by condenser (not shown),
Decompressor (not shown) and be delivered to cooler 66 (reference picture 4).
The compressor 100 so constituted is configured with compression unit 20 on the top of frame 24, and electronic list is configured with bottom
Member 30, frame 24 is flexibly supported in closed container 3 via disc spring 9.In this case, center of gravity is located at the height and position of frame 24
(with the position of the upper end of disc spring 9 with degree), therefore, it is possible to reduce the internal mechanism containing compression unit 20 and electrodynamic element 30
The deflection angle in 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 more effectively suppress in above-mentioned
The vibration in portion mechanism portion.Therefore, by the way that the vibration in internal mechanism portion can be suppressed, so as to reduce (the compression of internal mechanism portion
Unit 20 and electrodynamic element 30) clearance C L (reference picture 1) between closed container 3.As a result, closed container 3 can be reduced,
The miniaturization of compressor 100 can be realized.
In addition, in rubber base 10 (reference picture 1) of each order difference part 3a bottom provided with resilient support closed container 3.The rubber
Rubber base 10 is supported in the plate 11 fixed in the lower house 3n of closed container 3.In addition, rubber base 10 is in vertical (upper and lower
To) on be configured at the position overlapping with disc spring 9.Order difference part 3a is so formed, disc spring 9 is configured in order difference part 3a, so as to incite somebody to action
Disc spring 9 is arranged to not be soaked in the height of lubricating oil, therefore, it is possible to prevent noise that disc spring 9 is produced in lubricating oil internal vibration,
The quiet stabilisation of compressor 100 can be realized.In addition, the bottom by the way that rubber base 10 to be configured to order difference part 3a, Neng Goufang
Only the lower house 3n of rubber base 10 from closed container 3 is prominent greatly downwards, therefore, it is possible to suppress the height change of compressor 100
Height, can realize the miniaturization of compressor 100.
Next, 3~Fig. 5 of reference picture, fight to the finish and determine the distance between tie rods P and the unit of main axis length L relation of compressor 100 and enter
Row explanation.Fig. 3 is to represent the position dimension at each angle of inclination because of caused by gap when obtaining the interference rate of compressor
Illustrate figure, Fig. 4 is the chart for representing interference rate and COP relation, and Fig. 5 is the pass for representing interference rate and main axis length/distance between tie rods
The chart of system.In addition, Fig. 3 schematically illustrates the angle of inclination because of caused by each gap for ease of understanding.
In addition, as the COP (Coefficient Of Performance) for determining compressor will therefore one, Neng Goulie
Lift interference rate.The interference rate can be obtained by following formula (1).In addition, in the explanation of following formula (1), by bent axle
Referred to as axle, is referred to as bar by connecting rod, and cylinder barrel and journal bearing are referred to as into frame.In addition, α, β, γ, δ (not shown) are because of morpheme
Angle of inclination caused by tolerance, A, B, C, D, E are the angles of inclination because of caused by gap.In addition, for α~δ, being included with adding
Number record the diameter dimension of each part used in practice.
Interference rate=(alpha+beta+γ+δ)/(A+B+C+D+E) ... (1)
α：Angle of inclination (the main shaft φ 18- eccentric parts φ 15.9) because of caused by the depth of parallelism of bent axle
β：Angle of inclination (the big end φ 15.9- small ends φ 9.5) because of caused by the depth of parallelism of bar
γ：Angle of inclination (the external diameter φ 25.4- connecting holes φ 9.5) because of caused by the perpendicularity of piston
δ：Angle of inclination (the cylinder barrel φ 25.4- journal bearings φ 18) because of caused by the perpendicularity of frame
A：Frame (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-frame (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, 15.9mm is set to by big end 25b connecting hole 25b1 diameter, by small end 25a connecting hole
25a1 diameter is set to 9.5mm.The connecting hole 22a's that γ is the external diameter of the cylindrical portions of piston 22 with piston pin 29 is inserted is vertical
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 barrel of frame 24
The perpendicularity of 21 axial direction (diagram left and right directions) and the axial direction (diagram above-below direction) of journal bearing 26, as one, by cylinder
The internal diameter of cylinder 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 be due to the gap between the main shaft 23a of bent axle 23 and journal bearing 26 and main shaft 23a radially
Angle of inclination when bearing 26 is tilted.B be due between the big end 25b of connecting rod 25 and the eccentric part 23p of bent axle 23 between
Gap and angles of inclination of the eccentric part 23p when big end 25b is tilted.C is due to the small end 25a and piston pin 29 of connecting rod 25
Between gap and angle of inclination of the piston pin 29 when small end 25a is tilted.D is due to the company of piston pin 29 and piston 22
Tie hole 22a between gap and angle of inclination of the piston pin 29 when connecting hole 22a is tilted.E is due to piston 22 and frame
Gap between 24 cylinder barrel 21 and angle of inclination of the piston 22 when cylinder barrel 21 is tilted.
Then, when angle of inclination A, B, C, D, E according to Fig. 3 obtain tanA, tanB, tanC, tanD, tanE,
It can be represented with following formula (2)~(6).In addition, the unit in gap is micron, therefore, described in formula (2)~(6) " ×
1000 " are used to system of units synthesizing 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 be main shaft 23a and journal bearing 26 journal bearing 26 axial end (lower end) separation away from
From La is the sliding length for the main shaft 23a journal bearings 26 slided.CLb is eccentric part 23p and big end 25b in big end
The distance of 25b axial end (upper end) separation, Lb is the sliding length for the eccentric part 23p big end 25b slided.CLc
It is the distance of piston pin 29 and small end 25a in small end 25a axial end (lower end) separation, Lc is slided for piston pin 29
Dynamic small end 25a sliding length.CLd is the connecting hole 22a and piston pin 29 of piston 22 orthogonal with the axial direction of piston 22
Direction end (upper end) separation distance, Ld be for piston pin 29 slide connecting hole 22a sliding length.CLe is cylinder
Cylinder 21 and piston 22 are in the distance of the axial end separation of piston 22, and Le is that the slip of the cylinder barrel 21 slided for piston 22 is long
Degree.
When seeking A~E according to above-mentioned formula (2)~(6), then become 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)
So as to be indicated when each angle of inclination A~E is merged, then become formula (12) as shown below.
Arctan (each gap/(sliding length × 1000)) ... (12)
In addition, inquiring into according to the interference rate and COP relation obtained by above-mentioned formula (1), it is thus identified that can obtain following
Relation, i.e. as shown in figure 4, interference rate becomes lower, then COP becomes higher.It is thus identified that, the relation according to Fig. 4
Interference rate is sought, so as to improve the COP of compressor 100.
Therefore, Fig. 5 represents to contemplate multiple beyond by the angle of inclination A of the formula (1) relevant with the length of bent axle 23
When numeral is set to fixed value and makes main axis length L (reference picture 1) length change, main axis length L and distance between tie rods P (reference pictures
1) ratio (L/P) and the chart of the relation of interference rate.In addition, as described in Figure 1, the main axis length L in present embodiment refer to from
The main shaft 23a of bent axle 23 upper end, in other words, from flange part 23b lower surface 23b1, until the length of the lower end of journal bearing 26
Degree.As described in Figure 1, distance between tie rods P refers in the small end 25a of connection connecting rod 25 pivot c1 and big end 25b rotation
Heart c2 distance.Therefore, diminished by shortening main axis length L, L/P (main shaft length/distance between tie rods), by increasing main axis length L, L/
P becomes big.
As shown in Figure 5, it is thus identified that, as L/P becomes big, interference rate is uprised.In addition, it is thus identified that, it is near 1.1, to deposit in L/P
In flex point.I.e., it is thus identified that, in the case where L/P is less than 1.1, interference rate is converted 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, while interference rate can be reduced, master is shortened
Shaft length L.In addition, in the case where L/P is more than 1.1, as interference rate is uprised, main axis length L is elongated.Therefore, by by L/P
It is set as less than 1.1, shortens bent axle 23 and the miniaturization of machine 100 can be compressed, and be able to ensure that the property of compressor 100
Action failure (can prevent bent axle 23 from locking) and can be prevented.In addition, in the past, shortening main axis length L (compressor 100 is small-sized
Change) bearing load is become big, therefore do not use energetically up to now.But, it is thus identified that, even if main axis length L is shortened
Change, also can allow the increase of the increased bearing load along with bearing load by the way that L/P is set as into less than 1.1, energy
Enough ensure to be minimized while the performance as compressor 100.
In addition, the purpose of the performance in order to improve compressor 100, when by the mode of connection of piston 22 and connecting rod 25 from spherical
When joint is altered to piston pin mode, it is desirable to high dimensional accuracy.However, when shortening main axis length L, the inclination angle of bent axle 23
Degree becomes big, therefore, it is possible to relax the precision of form and position tolerance.In addition, by shortening main axis length L, being formed the fixation of bent axle 23
The bore hole 23c of axle portion part 23h insertions space narrows.Narrowed by the space, the region of cylindric thin-walled portion is also than song
Narrow in the case of axial length, therefore, it is possible to the corresponding rigidity for improving bent axle 23.By suppressing the flexural deformation of bent axle 23, even if
Shorten bent axle 23 and minimize compressor 100, can 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), by the way that main axis length L is set into 3~5 times of height H, the axial direction of piston pin 29 and main shaft 23a axial direction can be relaxed
The precision of the depth of parallelism of (central shaft O).Therefore, even if shortening bent axle 23 and minimizing compressor 100, it can also ensure that conduct
The performance of compressor 100.
Fig. 6 represents to be 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) is the structure that compressor is configured to top.
As shown in Fig. 6 (a), refrigerator 60A is configured to refrigerator main body 61 being divided into multiple receiving rooms 62,63,64,65.For example,
Receiving room 62 is refrigerating chamber, and receiving room 63 is upper strata refrigerating chamber, and receiving room 64 is lower floor's refrigerating chamber, and receiving room 65 is vegetable compartment.
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 the extraction of receiving room 65
The Machine Room of portion 65a depth side lower part (bottom of the rear side of refrigerator body 61).The refrigerant discharged from compressor 100
Heat in refrigerator is absorbed in cooler 66 by the condenser (not shown) in refrigerator 60A, the mechanism of decompressor (not shown),
And be back to herein in compressor 100.
If in addition, as ago applied high compressor, needing to increase the volume of Machine Room, therefore be accommodated in receiving room
65 lead division 65a capacity diminishes and (becomes shallow lead division).Therefore, by using the compressor for applying present embodiment
100 refrigerator 60A, can reduce the volume of Machine Room, can reduce the height and position of the top surface of Machine Room, therefore, it is possible to expand
The case inner capacities of the depth side of big accepting chamber 65.
In addition, as shown in Fig. 6 (b), compressor 100 is configured at depth upper lateral part (the refrigerator sheet of receiving room 62 by refrigerator 60B
The rear side of body 61 is topmost) Machine Room.
But, if as ago applied high compressor, refrigerator main body is delivered to due to the vibration that compressor is produced
Vibration also become big.Therefore, can be by above-mentioned by using the refrigerator 60B for the compressor 100 for applying present embodiment
Construct to reduce vibration, therefore, it is possible to suppress the vibration for passing to refrigerator main body 61.In addition, by applying small-sized compressor
100, the case inner capacities of receiving room 62 can be expanded.
Additionally, this invention is not limited to above-mentioned embodiment, it can carry out without departing from the scope of spirit of the present invention
Various changes.For example, distance illustrates to link the situation of piston 22 and connecting rod 25 with piston pin 29 in the present embodiment, still
It is not limited to piston pin 29, it would however also be possible to employ spherical combination.
Claims (3)
1. a kind of compressor, it possesses：Compression unit；Drive the electrodynamic element of above-mentioned compression unit；And store above-mentioned compression
The container of unit and above-mentioned electrodynamic element,
Above-mentioned compressor is characterised by,
Above-mentioned compression unit possesses：Cylinder barrel；By being moved back and forth and the piston of compression refrigerant in above-mentioned cylinder barrel；Pass through
Above-mentioned electrodynamic element and the bent axle for carrying out eccentric rotary；The eccentric part and above-mentioned piston of above-mentioned bent axle can rotatably be linked
Bar；And the bearing of the above-mentioned bent axle of supporting,
Axial length from the upper end of the main shaft of above-mentioned bent axle to the lower end of above-mentioned bearing is being set to L, above-mentioned bar will be connected
The pivot of one end and the distance of pivot of other end when being set to P, L/P is less than 1.1.
2. compressor according to claim 1, it is characterised in that
Above-mentioned compressor possesses the piston pin that can rotatably link above-mentioned piston and above-mentioned bar,
When the axial height of the end of above-mentioned piston pin is set into H, L/H is 3~5.
3. a kind of refrigerator, it is characterised in that possess the compressor described in claim 1 or 2.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016038095A JP2017155628A (en) | 2016-02-29 | 2016-02-29 | Compressor and refrigerator with this compressor |
| JP2016-038095 | 2016-02-29 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN107131109A true CN107131109A (en) | 2017-09-05 |
Family
ID=59721032
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710025343.7A Pending CN107131109A (en) | 2016-02-29 | 2017-01-13 | Compressor and the refrigerator for possessing the compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2017155628A (en) |
| CN (1) | CN107131109A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109372723A (en) * | 2018-12-11 | 2019-02-22 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and refrigerating plant with it |
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| 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 |
| JP2010281299A (en) * | 2009-06-08 | 2010-12-16 | Panasonic Corp | Sealed compressor |
| CN102057162A (en) * | 2008-07-31 | 2011-05-11 | 松下电器产业株式会社 | Closed type compressor |
| CN102200114A (en) * | 2011-06-17 | 2011-09-28 | 华意压缩机股份有限公司 | Super-efficient single-support compressor having taper hole bearing structure |
| CN203962319U (en) * | 2014-07-25 | 2014-11-26 | 浙江美亚特精密机械有限公司 | A kind of refrigeration compressor piston driving mechanism |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56175580U (en) * | 1980-05-30 | 1981-12-24 | ||
| JPS59130086U (en) * | 1983-02-18 | 1984-08-31 | 三洋電機株式会社 | Compressor oil supply system |
| DE10106234C2 (en) * | 2001-02-10 | 2002-12-12 | Danfoss Compressors Gmbh | piston compressor |
| JP2006220059A (en) * | 2005-02-10 | 2006-08-24 | Matsushita Electric Ind Co Ltd | Compressor |
-
2016
- 2016-02-29 JP JP2016038095A patent/JP2017155628A/en active Pending
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2017
- 2017-01-13 CN CN201710025343.7A patent/CN107131109A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN102057162A (en) * | 2008-07-31 | 2011-05-11 | 松下电器产业株式会社 | Closed type compressor |
| JP2010281299A (en) * | 2009-06-08 | 2010-12-16 | Panasonic Corp | Sealed compressor |
| CN102200114A (en) * | 2011-06-17 | 2011-09-28 | 华意压缩机股份有限公司 | Super-efficient single-support compressor having taper hole bearing structure |
| CN203962319U (en) * | 2014-07-25 | 2014-11-26 | 浙江美亚特精密机械有限公司 | A kind of refrigeration compressor piston driving mechanism |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109372723A (en) * | 2018-12-11 | 2019-02-22 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and refrigerating plant with it |
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| Publication number | Publication date |
|---|---|
| JP2017155628A (en) | 2017-09-07 |
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