CN1042564C - Electrically driven hermetic compressor - Google Patents
Electrically driven hermetic compressor Download PDFInfo
- Publication number
- CN1042564C CN1042564C CN 94106966 CN94106966A CN1042564C CN 1042564 C CN1042564 C CN 1042564C CN 94106966 CN94106966 CN 94106966 CN 94106966 A CN94106966 A CN 94106966A CN 1042564 C CN1042564 C CN 1042564C
- Authority
- CN
- China
- Prior art keywords
- piston
- cylinder
- relief opening
- compressor
- extension part
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Landscapes
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
An electrically driven hermetic compressor comprises a hermetic casing, an electric motor unit encased in the casing, and a compression mechanism encased by the casing and drivingly connected to the electric motor unit through a crankshaft. The compression mechanism includes a cylinder, a piston reciprocatingly slidable in the cylinder, a valve plate having formed therein a suction port and a discharge port and providing valve seats around the ports, suction valve and a discharge valve cooperating with the suction and discharge ports. The cylinder, the piston and the valve plate cooperate to define a compression chamber. The compressor further has a passage system providing separate passages for a gas to be compressed and the gas after compression, and a motion converting mechanism for converting rotary motion of the crankshaft into linear reciprocating motion of the piston. A frusto-conical projection is formed on the top of the piston at a point offset from the axis of the piston so as to be receivable in the discharge port which also is offset from the axis of the piston, thus minimizing dead volume when the piston has reached its top dead center of its stroke.
Description
The present invention relates to a kind of sealed electrical compressor, particularly a kind of with high compression efficiency running and sealed electrical compressor with good lubrication performance.Compressor of the present invention is specially adapted to the refrigerator and the air-conditioning refrigerator that move under no chlorine such as HFC134a refrigerant condition.
Common electrically driven hermetic reciprocating compressor, as the disclosed compressor of utility model patent No.2-132881 of Japanese unexamined, form a convex extension part at piston head, it can move into the relief opening in the seat board, thereby reduce the dead angle, improve compression efficiency with this.This convex extension part have one with the cylindrical body or the truncated cone of the coaxial formation of piston, or have one to form eccentric ring bodies with piston.
Be described with reference to Fig. 8 and 9 pairs of known sealed electrical compressors below.Fig. 8 is the cross-sectional view of known sealed electrical compressor, show the structure of compressor major component among the figure especially, and Fig. 9 is the sectional view of another kind of known sealed electrical compressor major component.
Referring to Fig. 8, compressor comprises a bent axle 1, piston 2, piston rod 3A, cylinder 4, a seat board 5, a relief opening 6, an intakeport 7, lid 18, air suction silencer passage 18a, exhaust cavity 18b and an exhaust passage 18c.
As can be seen from Figure, the connection between compressor piston 2 and the piston rod 3A adopts ball-and-socket joint to connect, and this ball-joint is as the device that rotatablely moving of bent axle 1 is converted to piston 2 straight reciprocating motions.When adopting this Connecting format, allow piston 2 around the longitudinal axis rotation of passing the ball-joint center.Even compressor design becomes to make convex extension part 2a on the piston and the relief opening 6 in the seat board 5 to depart from the form at the center of piston 2, rotation along with piston 2, convex extension part 2a can along the circumferential direction produce undesirable deflection, shift out the position of aiming at relief opening, the result, interfere owing between the piston convex extension part 2a that is offset and partial cylinders head or seat board, produce, thereby hindered the rotation of bent axle.This just must be with the reason of the convex extension part 2a on the piston with piston 2 coaxial settings.
Fig. 9 shows the structure of disclosed a kind of known compressor among the utility model patent No.2-132881 of Japanese unexamined.This compressor has a convex extension part 26 that is formed at piston 2A center portion.In this compressor, need big sealed gap that intakeport 7A and relief opening 6A are isolated mutually, the result has reduced the area of intakeport 7A, has increased harmful inhalation resistance.
In order to address this problem, as shown in Figure 9, adopted the structure of double suction gas port 7A.But, two intakepories are set, need the thickness of complex-shaped air intake passage and increase seat board 5A, so that obtain required intensity.
EP-0,513,475 disclose a kind of sealed electrical compressor, and its convex extension part is positioned at the relief opening opposite position with cylinder head, and the result produces such shortcoming, and promptly its structure is unsuitable for being used in the light duty compressor of refrigerator and air-conditioning refrigerator.In addition, at EP-0, in 513,475 the compressor, though improving to some extent aspect the reduction of the expansion-loss again of compressor and the volumetric efficiency, its lubrication property aspect is also not enough.
Therefore, the objective of the invention is to overcome above-mentioned shortcoming, a kind of sealed electrical compressor is provided, its structure is applicable to the light duty compressor of refrigerator and air-conditioning refrigerator, and has the good lubrication characteristic and can prevent from simultaneously to lower efficiency again.
According to an aspect of the present invention, it provides a kind of sealed electrical compressor, and this compressor comprises:
-sealing shell;
-be contained in the electric machine in the described shell;
-be contained in the described shell and be connected on the described electric machine and driven compressing mechanism by a bent axle;
Described compressing mechanism comprises a cylinder, one can make the piston that reciprocatingly slides in described cylinder, one valve plate, on this valve plate, form an intakeport and a relief opening, and around described suction, relief opening is equipped with valve seat, described compressing mechanism also comprises and described suction, the suction that relief opening matches, outlet valve, described cylinder, piston and valve plate complement each other to form a compression chamber, this compressing mechanism also comprises a lane device and a movement conversion mechanism, described lane device provides passage separately for the gas and the compression gas afterwards that will compress, described movement conversion mechanism converts the rotation motion of bent axle to the straight reciprocating motion of described piston
Wherein, form a convex extension part departing from position of described piston axis piston head, so that insert in valve plate in the formed relief opening this convex extension part.
Circular cone shape can be made in the convex extension part of piston head, and relief opening also can be made taper, protrudes out the tapering of the tapering of the conical surface less than the relief opening conical surface.
Movement conversion mechanism is an a kind of dog link type mechanism, and it has one to be the slip pipe and a slider of one with piston, and slider is connected with the eccentric part of bent axle, and can slidably reciprocate in slip pipe.Formed intakeport is arranged on towards the position of piston crimping section deviation in driction cylinder-bore axis on the valve plate, and the crimping section of piston is meant that pressure acts on the piston portion on the cylinder wall because piston produces with respect to cylinder-bore axis.The convex extension part that is piston head is arranged on the position of departing from piston axis towards piston crimping section opposite direction.
In having the sealed electrical compressor of described feature, the convex extension part of piston head and the relief opening in the valve plate depart from piston axis, like this, have obtained enough big sealed gap between suction, exhaust passage.In addition, although be provided with the convex extension part at piston head, suction, relief opening still have very big cross sectional area.
This and other purpose, characteristics and the advantage of going up of the present invention is by hereinafter description taken together with the accompanying drawings can be more cheer and bright.Wherein:
Fig. 1 is an embodiment's of a sealed electrical compressor of the present invention sectional view, shows in detail the structure of its main compressing mechanism among the figure;
Fig. 2 is the longitudinal sectional view of compressor shown in Figure 1;
Fig. 3 is the pressure-volume curve figure of compressor operating shown in Figure 2;
Fig. 4 is another embodiment's of a sealed electrical compressor of the present invention sectional view, shows in detail the major component of compressing mechanism among the figure;
Fig. 5 is another embodiment's of a sealed electrical compressor of the present invention sectional view, shows in detail the structure of compressor compresses mechanism major component among the figure;
Fig. 6 A is the structural drawing of compressing mechanism among Fig. 5 to 6D, there is shown a cyclic process of compressing mechanism operation, comprises suction stroke, compression stroke and exhaust stroke;
Fig. 7 is a refrigeration cycle skeleton diagram, there is shown an application example of sealed electrical compressor of the present invention;
Fig. 8 is the sectional view of the main compression mechanism section of known sealed electrical compressor; And
Fig. 9 is the sectional view of another kind of known motor compressor compressing mechanism major component.
Below with reference to Fig. 1 basic principle of the present invention is described, Fig. 1 is an embodiment's of a sealed electrical compressor of the present invention sectional view, there is shown the structure of compressing mechanism major component.
Among Fig. 1, implement sealed electrical compressor of the present invention and have a linkage-type arrangements, this mechanism converts the linearity of piston 2 or the device of straight reciprocating motion to as the rotation motion with bent axle 1.In this bindiny mechanism, utilize a bearing pin 8 that bar 3 and piston 2 are articulated, to prevent piston 2 around its axis, also, and the rotation of the axis of cylinder 4, cylinder 4 is holding piston 2 slidably.The top of piston 2 is formed with a convex extension part 2a.Convex extension part 2a is suitable for inserting in the relief opening 6 during near the upper dead center of its stroke at piston 2.Consider the gap between bar 3 and the bearing pin 8, thereby the center that makes convex extension part 2a and relief opening 6 depart from piston.According to this structure, can not produce for example because of the misalignment between caused convex extension part 2a of rotatablely moving of piston 2 and the relief opening 6, thereby, can not take place owing to piston 2 rotates the rotation that interference between caused piston and the cylinder head hinders bent axle around himself axis.Because relief opening 6 departs from the center of piston, thus make inhale, obtain enough big sealed spacer between the exhaust passage and obtain big suction, the relief opening cross sectional area becomes possibility.
The present invention has realized making the target of dead volume minimum like this, this also is the purpose that the convex extension part is set at piston head, and can not occur as the problem that reaches, the relief opening cross sectional area is restricted, therefore, reduce loss in efficiency and owing to expand the again capacity that causes of pressurized gas reduces, thereby improved compressor efficiency.
Below with reference to Fig. 1 to 7 embodiments of the invention are described.
Fig. 2 is the longitudinal sectional view of sealed electrical compressor of the present invention, and Fig. 3 is the pressure-volume curve figure of expression compressor operating performance shown in Figure 2.Compressor shown in Figure 2 has comprised compressing mechanism described in conjunction with Figure 1.Among Fig. 1 and 2, know that with shown in Figure 8 compressor components identical or assembly represented by identical label.
Sealed electrical compressor shown in Figure 2 has an airtight shell 10, and electric machine 11 and compressing mechanism 12 are housed in shell 10, and both are interconnected by bent axle 1.The compression assembly of electric machine 11 and compressing mechanism 12 are supported by resilient supporting unit such as spring by outer casing bottom.
Electric machine 11 has one to be fixed to the stator 11a on the support 15 and to be fixed to rotor 11b on the bent axle 1 by shrink fit by the bolt (not shown).Above-mentioned bracket bearing 15a links to each other with support 15, thus supporting crankshaft 1 rotatably.
As illustrated in fig. 1 and 2, compressing mechanism 12 have a cylinder 4, be contained in slidably can be reciprocating in the cylinder 4 a piston 2 and a valve plate 5, valve plate 5 has an intakeport 7 and a tool relief opening 6 that forms on it.Cylinder 4, piston 2 and valve plate 5 form compression chamber 4a.The suction, the exhaust passage that link to each other with 6 with suction, relief opening 7 respectively again that compressing mechanism 12 separates each other in addition.
In addition, also is furnished with the mechanism that the rotation motion of bent axle 1 is converted to the straight reciprocating motion of piston 2.Exactly, this mechanism comprises a connecting rod 3 (being called for short " bar ") and a wrist pin 8, and bar 3 has a bearing part around bent axle 1 eccentric part 1a, by wrist pin 8 bar 3 is received on the piston 2.This mechanism converts the rotation motion of bent axle 1 to according to known mode the straight reciprocating motion of piston 2.
As shown in Figure 1, the position of departing from the piston center at the top of piston 2 is provided with a convex extension part 2a, and when moving to upper dead center position near its stroke with convenient piston 2, this convex extension part 2a can insert in the relief opening 6 that forms in the valve plate 5.Like this, convex extension part 2a on the piston 2 and relief opening 6 all depart from the axis of piston 2, and the result can not interfere between piston convex extension part 2a and the valve plate 5 when compressor operating.In addition, relief opening 6 departs from the axis of piston 2, and this makes the cross-section area of suction, relief opening design to such an extent that become possibility more greatly.
The running of compressing mechanism is as follows: along with the downward stroke of piston 2, piston 2 promptly shown in Figure 1 has been set up negative pressure towards the motion on the right side in cylinder 4, and like this, Aspirating valves 16 is opened.Then, import in the sealing shell 10 through sucking pipe 10a by gas by compression, and suck compression chamber 4a by inhaling silencer passage 18a, intakeport 7 and Aspirating valves 16.After this, piston 2 begins making progress of it from lower dead centre, and promptly towards the stroke on a left side, like this, the pressure among the compression chamber 4a raises and closes Aspirating valves 16.The volume of compression chamber 4a further reduces, and gas pressure continues to raise.When gas pressure reached scheduled pressure value, outlet valve 17 was opened, and gas is discharged into the exhaust cavity 18b that covers in 18 through relief opening 6, and this process just finishes when piston 2 arrives upper dead center.The gas of discharging is guided to the outside of sealing shell 10 through exhaust passage 18c.Along with the continuation of bent axle 1 rotation, described air-breathing, compression and exhaust stroke move in circles and carry out.
Below with reference to P-V curve (pressure-volume curve) shown in Figure 3 above-mentioned cyclic process is described.In this plotted curve, Td represents upper dead center, and Bd represents lower dead centre, and Dv represents dead volume, and Dp represents displacement, and As represents real suction, the Re institute's work of representing to expand again of showing.Even its upper dead center Td of piston arrives, the volume of compression chamber 4a can not be reduced to zero yet.In other words, certain volume comprises the volume of relief opening inboard, even still remain unchanged after the piston arrives upper dead center.This volume so-called " dead volume " Dv, it can not be discharged from.Like this, still keeping in the compression chamber 4a not do not discharge, pressure is the gas of exhaust pressure Pd, this part gas pressure in suction stroke is subsequently reduced to pressure of inspiration(Pi) Ps and is produced adiabatic expansion.Like this, what the suction of live gas Vc in Fig. 3 was represented a bit begins, the result, and the actual volume that sucks has reduced.When compressor was used in the refrigerator, this gas expanded and has reduced the efficient of refrigerator nocuously, and when compressor was used as vacuum pump, it had reduced the absolute value of attainable degree of vacuum again.
Can be reclaimed by the gas work Re of institute (by piston institute work, using the cross hatched regions domain representation among Fig. 2 before the compression stroke) part that expands again, as the energy of downward promotion piston, this helps machine operation.But some merit can not reclaim and cause so-called expansion-loss again.Like this, dead volume has not only reduced compressor capacity (gas discharge rate), and has reduced the efficient of compressor.
When compression ratio (Pd among Fig. 3) was big, volume Vc and expansion work increase more like this, had seriously influenced the efficient and the capacity of compressor.Therefore, it is very important reducing dead volume, especially when system that compressor is used for moving under the big pressure ratio condition, when for example being used in refrigerator and the air conditioner, all the more so.
In the compressor of typical refrigerator, discharge capacity is little of 5ml, and the internal diameter of corresponding cylinder 4 is also smaller, for example about 20mm.In air conditioner, the discharge capacity of compressor is usually big to being 3 to 4 times of refrigerator compressor displacement, and cylinder bore diameter is still little of being about 20mm, and its reason is, uses a pair of cylinder in this case usually, so that raise the efficiency, elimination is simultaneously vibrated.In the border circular areas of this little cylinder bore diameter, also the diameter of relief opening 6 must be designed to 3～4mm in addition, the diameter of intakeport 7 is designed to 7～8mm, and inhale, relief opening also needs to be spaced from each other by lid 18, its sealed gap is 3～4mm at least.Moreover, consider reliability, also must limit the lift angle of Aspirating valves 16 and outlet valve 17.Therefore relief opening 6 need be arranged on the position of departing from piston 2 axis.
In this embodiment, consider between pin 8 and the bar 3, between bar 3 and the bent axle 1, between bent axle 1 and the support 15 and have mechanical clearance between piston 2 and the cylinder 4, the convex extension part 2a at piston 2 tops is made the center of departing from piston 2, and it is corresponding with the biasing of relief opening 6, like this, convex extension part 2a can insert in the relief opening 6, thus, residual volume when having reduced the piston arrives upper dead center in the relief opening, this volume also is one of principal element that produces dead volume, as a result, eliminated again and expanded, obtained bigger capacity and higher hermetic type compressor efficient.
In sum, in the first embodiment of the present invention, the convex extension part 2a at piston 2 tops and relief opening 6 all depart from the axis of piston, the result, although be provided with convex extension part 2a, still kept long sealed spacer, and obtained enough big suction, relief opening cross sectional area.Therefore, the dead volume that make to reduce in the relief opening 6 becomes possibility, has eliminated the restriction to suction, exhaust passage simultaneously, has so also got rid of by the pressurized gas minimizing of caused energy loss and capacity of expanding again, thereby has improved the efficient of compressor.
Intakeport 7 is designed to can further improve gettering efficiency like this along the lengthening flute profile of piston axis extension.
Fig. 4 is the longitudinal sectional view of sealed electrical compressor second embodiment's of the present invention compressing mechanism major component.Use the label identical to represent with employed identical part of first embodiment or assembly, thereby omit the detailed description of or part individual these groups with Fig. 1.
Convex extension part embodiment illustrated in fig. 4 is different with embodiment 1, represents with 2B, and a truncated cone is arranged at the top of piston, and its tapering or gradient are less than the tapering or the gradient of the wall that forms relief opening 6.More precisely, in this embodiment, the axis that departs from piston 2 with relief opening that 6B marked and convex extension part 2B.The wall that forms relief opening 6B is taper, and to the relief opening end that is adjacent to exhaust cavity 18b, the diameter of relief opening reduces gradually, will insert the taper angle theta of the convex extension part 2B frustum of relief opening 6B from the relief opening end that is adjacent to piston
1Taper angle theta less than relief opening 6B
2
Usually, when the convex extension part of piston head move into relief opening refrigerant when cylinder is discharged, because the cross sectional area of exhaust passage reduces, thereby the speed of discharging gas becomes very high, the result, and gas has run into the resistance that becomes big, pressure in the cylinder is too raise, like this, increased the overcompression loss, i.e. the useless energy that causes gas compression to produce owing to unnecessary high pressure values.Therefore, the convex extension part of piston head and the gap between the relief opening are too little can to lower efficiency nocuously, and this impairs at piston head the desired benefit that obtains in convex extension part is set.Therefore, although there are many aspects to need to consider when setover as described above like that in the convex extension part of piston, what serious problems is these aspects can not cause.
In the embodiment shown in fig. 4, the convex extension part 2B of piston head is a truncated cone, and the tapering of its conical surface is made the form less than the tapering of the relief opening 6B conical surface.
This second embodiment has the identical advantage with aforementioned first embodiment, thereby has the advantage that the exhaust gas region that has kept enough spaciousnesses has reduced overcompression in addition.
Fig. 5 is the longitudinal sectional view of the major component of sealed electrical compressor the 3rd embodiment's compressing mechanism of the present invention.Fig. 6 A to 6D is air-breathing, the compression finished of compressing mechanism shown in Figure 5 and the schematic representation of exhaust stroke.In these figure, use with Fig. 1 in identical label represent components identical or assembly, it is described in detail referring to embodiment 1, no longer repeats here.
Compressor shown in Figure 5 has one to be the slip pipe 2c and a cylinder slider 19 of one with piston 2, and cylinder slider 19 links to each other with the eccentric part 1a of bent axle 1, and can slide in slip pipe 2c.Slip pipe 2c and slider 19 are combined and are formed a mechanism, and so-called " dog link type mechanism ", it converts rotatablely moving of bent axle 1 to the linear reciprocating motion of piston 2.
This embodiment and previous embodiment 1 are the same with 2 situation, have also avoided the rotation of piston 2 with respect to cylinder 4, and like this, convex extension part 2a can be arranged on and depart from piston 2 axial location places, and the danger that interferes between convex extension part 2a and the valve plate can not occur.
More detailed structure can be referring to Fig. 6 A to 6D, and R represents refrigerant among the figure, and L represents lubricant oil, and M represents mist of oil.Fig. 6 A to 6D is the structural drawing from the dog link type compressing mechanism of sealed electrical compressor top view.In an operation cycle process of piston, piston to-and-fro motion between upper dead center (Fig. 6 A) and lower dead centre (Fig. 6 C), suction stroke (referring to Fig. 6 B) and compression stroke (Fig. 6 D) have been finished simultaneously, in the meantime, because slip pipe 2C and piston 2 are one, therefore allow piston 2 axis tilt with respect to cylinder 4 in by the formed angular range in gap between cylinder 4 inwalls and the piston 2.
Because piston 2 is with respect to the axis tilt of cylinder 4, therefore, the wall of piston 2 top 2d and cylinder 4 keeps in touch, and the another part just in time opposite with this part 2d and the lower edge 4b of cylinder 4 keep in touch.
The lubricant oil that is fed to piston 2 and cylinder 4 mainly adopts following two kinds of approach to supply with: promptly, from being splashed to bent axle 1 top and space on every side by 1 lubricant mist that sprays, suck in the cylinder 4 through air intake passage 18a again, thereby the zone between the wall of lube pistons 2 edge 2d and cylinder 4, and another part mist of oil arrives the outer surface of piston 2, so that the zone between the lower edge 4b of primary lubricant cylinder 4 and the piston 2.Because the temperature of refrigerant raises in compression process, pressure load acts on the top of piston 2, and therefore, the edge 2b of piston 2 and the zone between the cylinder wall surface are topmost to the demand of lubricant oil.Although cylinder-bore axis and crankshaft center line depart from a segment distance E each other, as shown in Figure 6A,, the side loading that is imposed on the cylinder wall matching surface by piston edge 2d can not be reduced to zero.
In this embodiment, intakeport 7 is towards the end biasing that is adjacent to piston edge 2d, like this, the zone that is adjacent to edge 2d by the compressor air suction stroke during through the cryogenic coolant cooling of intakeport 7 inspirations.Simultaneously, lubricant oil departs from the zone that the convex extension part 2a of piston 2 axis is connected with piston owing to surface tension is deposited on, and during compression stroke, the lubricant oil of deposition is supplied to the end of piston 2, thus, has avoided the generation of wearing and tearing, thereby has improved reliability.
Can find out that from the description of front the first and the 3rd embodiment has improved the reliability of sealed electrical compressor.
When compressor of the present invention was used in the following example, the advantage that aforementioned several embodiment brought can be more remarkable:
Traditional refrigerant that is used in refrigerator or the air-conditioning refrigeration system is freon class refrigerant.For example, use CFC12 usually in the refrigerator, and use HCF22 in the room air conditioner usually.This class refrigerant is dissolvable in water in the lubricant oil, has reduced oil body, therefore impairs the reliability of sliding parts.Contain chlorine in the molecule of this class refrigerant.When utilizing this refrigerant under the sliding condition of difficulty, it can decompose and produce chlorine, and the metal surface of chlorine and sliding parts reacts, produce a kind of compound as, ferric chloride like this, forms a kind of compound oil film.The ferric chloride oil film has self lubricity, can be used as the extreme pressure additive, in case the killing of sliding stop part, this helps to improve the reliability of compressor.
But in recent years, for using chloride freon class refrigeration agent to limit, this was because monomer chlorine can destroy tellurian ozonosphere by pertinent regulations, through having discovered the substitute refrigerants that does not conform to chlorine.HFC134a is exactly a kind of of this class substitute refrigerants.But when this substitute refrigerants was used in the refrigeration cycle, itself presented bigger difference between exhaust pressure and pressure of inspiration(Pi), caused compressor to move under the sliding condition of difficulty.In addition, because not chloride substitute refrigerants can not form any selflubricating oil film, therefore, this class refrigerant is to preventing the effect of not killed of sliding parts, and the result has reduced the reliability of compressor.
And the several embodiments' of aforementioned the present invention sealed electrical compressor, by lubricating condition and the cooling effect that improves the piston sliding area, make the compressor can safe operation under with this not chloride refrigerant condition, this makes and utilizes substitute refrigerants such as HCL134a to become possibility.
Like this, in aforementioned the 3rd embodiment, utilized dog link type mechanism to convert rotation motion to to-and-fro motion.In this embodiment, intakeport is towards the deviation in driction cylinder-bore axis of the edge 2d of aforementioned piston, the edge 2d of piston is the part of sliding on cylinder wall at the pressure maximum lower piston, and the convex extension part on the piston is at the axis of the deviation in driction cylinder opposite with intakeport, like this, greasy property in the peripheral region, the above-mentioned edge of piston and cooling effect have obtained improving greatly, and compressor has obtained higher reliability.
According to the regulation of restriction use freon refrigerant, under the condition of the substitute refrigerants of using self-lubricating effect to reduce, when for example in the sealed electrical compressor of refrigerator, using HFC134a type refrigerant, obtained special obvious effects.
Above-mentioned advantage all is that sealed electrical compressor itself obtains.When this compressor is used in the system, for example be used in the refrigeration cycle of air conditioner, the present invention also has following advantage.
Fig. 7 is the refrigeration cycle skeleton diagram of refrigerator or room air conditioner, and H represents heat among the figure.This refrigeration cycle with combine with the represented sealed electrical compressor of the present invention of label 20.
As can be seen from Figure 7, refrigeration cycle comprises the condenser 21 that links to each other with compressor 20 outlets, damping mechanism that links to each other with condenser 21 outlet sides or expansion valve 22 and the vaporizer 23 that links to each other with expansion valve 22 outlets.The outlet end of vaporizer 23 links to each other with the inlet side of compressor 20.
Compressor 20 is used for compressing the refrigerant gas that is enclosed in the refrigeration cycle, with the pressure and temperature of raising refrigerant gas, thereby circulates this gas.Because refrigerant carries out heat exchange with the another kind of thermal medium that flows through condenser 21 in condenser 21, so refrigerant becomes liquid phase in this condenser 21.Liquid phase refrigerant is introduced in the expansion valve 22, with pressure and its temperature of reduction that reduces it, after this evaporates by the absorbing environmental temperature in vaporizer 23, and converts gas phase to, then by compressor gas is sucked and compresses.Like this, refrigerant circulates through the closed loop of refrigeration cycle, becomes gas phase from liquid phase simultaneously, vice-versa.Saturation pressure under temperature when therefore, the compression ratio Pd/Ps of compressor is condensed into liquid phase by refrigerant is determined.Do in the refrigerator of refrigerant at the common CFC12 that utilizes, compression ratio is up to 10～12, and utilizes HFC134a to do in the air conditioner refrigerator of refrigerant, and compression ratio is about 3～4.When use satisfying the aforementioned no chlorine refrigerant HFC134a of regulation in refrigerator, compression ratio can further be elevated in the scope between 11 and 13.In sum, compressor of the present invention is used in the very big system of compression ratio as the aforementioned in the refrigerating circulation system time, its advantage is significant especially.
Although the advantage to indivedual most preferred embodiments is described, concerning those skilled in the art, clearly, these embodiments can independences or are used in combination, and like this, these embodiments' advantage is at double.
Understand from noted earlier, according to the present invention, reach minimum by formed dead volume in piston head formation convex extension part makes relief opening and become possibility, suffered various restrictions in the design of suction, exhaust passage etc. have been eliminated simultaneously, like this, also eliminated by the pressurized gas minimizing of caused loss in efficiency and capacity of expanding again, thereby obtained high efficiency sealed electrical compressor.
Compressor of the present invention is by reducing to dead volume minimum its efficient that improved, this compressor can be used as needs and obtains the vacuum pump of extra high degree of vacuum or as the compressor in the refrigeration cycle, and this refrigeration cycle operates under the situation of refrigeration cycle of difference is bigger between suction, the exhaust pressure situation such as refrigerator and room air conditioner.
Claims (3)
1. sealed electrical compressor comprises:
-sealing shell;
-be contained in the electric machine in the described shell, and
-be contained in the described shell and be connected on the described electric machine and driven compressing mechanism by a bent axle;
Described compressing mechanism comprises a cylinder, one piston that can in described cylinder, reciprocatingly slide, one valve plate, on this valve plate, form an intakeport and a relief opening, and around described suction, relief opening is furnished with valve seat, this compressing mechanism also comprises and described suction, the suction that relief opening matches, outlet valve, described cylinder, piston and valve plate cooperate formation one compression chamber, described compressing mechanism also comprises a lane device and a movement conversion mechanism, described lane device provides passage separately for the gas and the compression gas afterwards that will compress, described movement conversion mechanism converts the rotation motion of bent axle to the straight reciprocating motion of piston
It is characterized in that,
On position of the piston head that departs from described piston axis, form a convex extension part, so that making this convex extension part inserts in valve plate in the formed relief opening, described intakeport and relief opening are positioned to along the diametric(al) of described piston relative to each other, and the tapering of the described convex extension part conical surface is less than the tapering of the relief opening conical surface.
2. sealed electrical compressor according to claim 1 is characterized in that, described movement conversion mechanism is an a kind of dog link type mechanism, it has one to be the slip pipe and a slider of one with piston, slider links to each other with the eccentric part of bent axle, and can slidably reciprocate in slip pipe, and
Wherein, at the intakeport of the above one-tenth of valve plate axis towards the described cylinder of deviation in driction of described piston top edge crimping section, the crimping section of piston is meant the piston portion that pressure is affacted institute's art cylinder wall, and the convex extension part on the described piston head is departed from the axis of piston together towards the side opposite with described piston crimping section.
3. sealed electrical compressor according to claim 1, it is characterized in that, described movement conversion mechanism is a linkage-type arrangements, comprise a connecting rod, one end of this connecting rod is pivotally attached to the eccentric part of bent axle, and its other end links to each other with piston by a pin that is installed on the described piston, and
Wherein, the intakeport that forms on described valve plate is towards the axis of the described cylinder of deviation in driction of the crimping section at piston edge, the crimping section of piston is meant pressure is applied to piston portion on the cylinder wall that the convex extension part of piston head is towards the axis of the deviation in driction piston opposite with the piston crimping section.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP116707/93 | 1993-05-19 | ||
| JP11670793A JP3205122B2 (en) | 1993-05-19 | 1993-05-19 | Hermetic electric compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1098477A CN1098477A (en) | 1995-02-08 |
| CN1042564C true CN1042564C (en) | 1999-03-17 |
Family
ID=14693839
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 94106966 Expired - Lifetime CN1042564C (en) | 1993-05-19 | 1994-05-19 | Electrically driven hermetic compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP3205122B2 (en) |
| CN (1) | CN1042564C (en) |
Families Citing this family (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| IT243422Y1 (en) * | 1997-05-26 | 2002-03-04 | Zanussi Elettromecc | COMPRESSOR EQUIPPED WITH PERFECTED PISTON |
| CN1095939C (en) * | 1997-11-13 | 2002-12-11 | Lg电子株式会社 | Piston connection device for sealed compressor |
| KR100739550B1 (en) * | 2001-12-11 | 2007-07-16 | 엘지전자 주식회사 | Multi capacity compressor |
| KR100922213B1 (en) * | 2003-06-13 | 2009-10-20 | 엘지전자 주식회사 | Hermatic compressor |
| CN100344876C (en) * | 2003-06-25 | 2007-10-24 | 乐金电子(天津)电器有限公司 | Connection structure of crankshaft and connecting rod for compressor |
| BRPI0505717B1 (en) * | 2005-12-16 | 2020-03-10 | Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda | HERMETIC COMPRESSOR WITH INTERNAL THERMAL INSULATION |
| JP5533061B2 (en) | 2009-06-12 | 2014-06-25 | パナソニック株式会社 | Hermetic compressor and refrigeration system |
| JP5617402B2 (en) * | 2010-07-15 | 2014-11-05 | パナソニック株式会社 | Reciprocating compressor and refrigerator using the same |
| NL1038701C2 (en) * | 2011-03-23 | 2012-09-25 | Aqua Gutta B V | Device for extracting humid from air by using a wind-turbine in combination with a mechanically driven heat-pump system, as well as heat-pump system applicable with such a device. |
| JP6065192B2 (en) | 2011-05-09 | 2017-01-25 | パナソニックＩｐマネジメント株式会社 | Hermetic compressor |
| BR102012025279B1 (en) * | 2012-10-03 | 2021-09-21 | Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda | REFRIGERATION COMPRESSOR HAVING A GAS DISCHARGE SYSTEM |
| WO2017034983A1 (en) * | 2015-08-26 | 2017-03-02 | Carrier Corporation | Reciprocating compressor vented piston |
| CN106698158A (en) * | 2017-02-23 | 2017-05-24 | 惠安盛泽建材有限公司 | Ventilation management system based on Internet of Things and used for elevator |
| CN107378575B (en) * | 2017-08-24 | 2023-08-22 | 黄石华旦机械制造有限公司 | Tool for cutting crankshaft positioning groove |
| CN108343607B (en) * | 2018-02-02 | 2024-01-05 | 广东美芝制冷设备有限公司 | Compression mechanism and compressor with same |
| JP6928192B1 (en) * | 2021-05-12 | 2021-09-01 | 株式会社三井Ｅ＆Ｓマシナリー | Piston pump |
| CN113550888B (en) * | 2021-07-27 | 2023-02-10 | 福建空分气体有限公司 | Compression cylinder structure for piston compressor |
-
1993
- 1993-05-19 JP JP11670793A patent/JP3205122B2/en not_active Expired - Fee Related
-
1994
- 1994-05-19 CN CN 94106966 patent/CN1042564C/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH06323251A (en) | 1994-11-22 |
| CN1098477A (en) | 1995-02-08 |
| JP3205122B2 (en) | 2001-09-04 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1042564C (en) | Electrically driven hermetic compressor | |
| US5816783A (en) | Electrically driven hermetic compressor | |
| KR19980070415A (en) | compressor | |
| EP0943802A3 (en) | Variable capacity swash-plate compressor with oil separator | |
| CN1115485C (en) | Hermetic compressor | |
| JP2004522037A (en) | Piston lubrication system for reciprocating compressor with linear motor | |
| CN1779236A (en) | Compressor | |
| JP2000097149A (en) | Swash plate type compressor | |
| JPS5849433Y2 (en) | Rotating swash plate compressor | |
| JP3017123B2 (en) | Compressor | |
| KR0175879B1 (en) | Piston apparatus of a reciprocating compressor | |
| US6568913B1 (en) | Lubrication pump for a swash plate type compressor | |
| KR20010016078A (en) | a rotating compressor with an inclined shaft and multi-exhaust systems | |
| KR102579202B1 (en) | Reciprocating compressor | |
| CN1118632C (en) | Fluid machinery | |
| JP2004204683A (en) | Compression method for oil-free reciprocating compressor | |
| CA2511140A1 (en) | Rocker compressor mechanism | |
| CN1186165A (en) | Closed type compressor | |
| KR200177719Y1 (en) | Air compressor | |
| KR970006903A (en) | compressor | |
| KR200153706Y1 (en) | Reciprocating compressor | |
| KR200370491Y1 (en) | Multiple cylinder hermetic compressor | |
| KR20090041715A (en) | Linear compressor | |
| KR100653622B1 (en) | Multiple cylinder hermetic compressor | |
| JPH02230983A (en) | Piston slide type vacuum pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CX01 | Expiry of patent term |
Expiration termination date: 20140519 Granted publication date: 19990317 |