CN104595195A - Low-backpressure rotary type compressor - Google Patents

Low-backpressure rotary type compressor Download PDF

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Publication number
CN104595195A
CN104595195A CN201410737860.3A CN201410737860A CN104595195A CN 104595195 A CN104595195 A CN 104595195A CN 201410737860 A CN201410737860 A CN 201410737860A CN 104595195 A CN104595195 A CN 104595195A
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CN
China
Prior art keywords
slide plate
plate chamber
cylinder
oil
chamber
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Granted
Application number
CN201410737860.3A
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Chinese (zh)
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CN104595195B (en
Inventor
高斌
喻继江
郭宏
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Guangdong Midea Toshiba Compressor Corp
Guangdong Meizhi Compressor Co Ltd
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Guangdong Meizhi Compressor Co Ltd
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Priority to CN201410737860.3A priority Critical patent/CN104595195B/en
Publication of CN104595195A publication Critical patent/CN104595195A/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

A disclosed low-backpressure rotary type compressor comprises a housing, a compression mechanism, an oil separator for performing oil-gas separation on a refrigerant discharged from a cylinder, and an oil pool for holing lubricating oil separated from the oil separator; the compression mechanism comprises a cylinder assembly, a piston, a slide sheet, a main bearing and an auxiliary bearing; the cylinder possesses a slide-sheet chamber, the slide-sheet chamber is provided with an oil supply hole, and when the slide sheet makes reciprocated motions, the tail end of the slide sheet stretches into or out of the slide-sheet chamber so as to enable the internal capacity of the slide-sheet chamber to be varied between a maximum capacity V2 and a minimum capacity V1; and the oil pool is communicated with the oil supply hole via a slide-sheet oil supply path, and the ratio of the maximum capacity V2 and the minimum capacity V1 satisfies the following relationship: 35%<=V1/V2<=85%. According to the low-backpressure rotary type compressor, the pressure fluctuation of the slide-sheet chamber is not too large or too small, clinging seal between the slide sheet and the piston is guaranteed, and when the stress demand of the slide sheet is relatively well satisfied, relatively good compressor performances are realized.

Description

Low backpressure rotary compressor
Technical field
The present invention relates to compressor field, especially relate to a kind of low backpressure rotary compressor.
Background technique
In low backpressure rotary compressor, due to the pressure of inspiration(Pi) environment that enclosure interior is low pressure, the gas force acting on slide plate tail end is not enough to the close contact ensureing slide plate tip and piston external diameter, therefore, the zone design at slide plate tail end place is needed to form the slide plate chamber with housing inner diameter sealed separation, and provide relative hyperbaric environment, to ensure the close contact of slide plate tip and piston external diameter to slide plate chamber.Further, because slide plate chamber needs and enclosure interior sealed separation, the oil sump of enclosure interior cannot be utilized to realize lubrication, therefore, also need slide plate chamber fuel supply path reasonable in design, ensure lubrication and the sealing of slide plate.
In addition, in airtight slide plate chamber, due to the to-and-fro motion of slide plate, the volume in slide plate chamber also can cyclically-varying thereupon, in this change procedure, when the volume in slide plate chamber is minimum, there is maximum value in the pressure in slide plate chamber, and when the volume in slide plate chamber is maximum, there is minimum value in the pressure in slide plate chamber.If the structural capacity design in slide plate chamber is unreasonable, may occur when the pressure maximum in slide plate chamber is excessive, the power consumption of compressor is brought to rise, even cause current anomaly ambassador Motor shut down exceptionally, also may occur when the pressure minimum in slide plate chamber is too small, the close contact of slide plate tip and piston external diameter cannot be ensured, cause slide plate and piston to occur clashing into and produce abnormal sound and inordinate wear, and occur that leakage causes compressor performance to worsen.
Summary of the invention
The present invention is intended to solve one of technical problem in correlation technique at least to a certain extent.For this reason, the present invention proposes a kind of low backpressure rotary compressor, and the pressure surge in slide plate chamber can not be excessive or too small.
According to the low backpressure rotary compressor of the embodiment of the present invention, comprising: housing, described housing is provided with relief opening and gas returning port, compressing mechanism, described compressing mechanism is located in described housing, described compressing mechanism comprises cylinder assembly, piston, slide plate, main bearing and supplementary bearing, described main bearing and described supplementary bearing are located in the both ends of the surface of described cylinder assembly respectively, described cylinder assembly comprises at least one cylinder, a described piston is provided with in each described cylinder, the tip of described slide plate is only against on the periphery wall of described piston, described cylinder also has slide plate chamber, described slide plate chamber has oil supply hole, when described slide plate moves back and forth, the tail end of described slide plate stretches into or stretches out described slide plate chamber and changes between maximum volume V2 and minimum volume V1 to make the internal capacity in described slide plate chamber, for carrying out the oil separator of Oil-gas Separation to the refrigerant of discharging from described cylinder, for holding the oil sump of the lubricant oil that described oil separator is separated, described oil sump is communicated with described oil supply hole by slide plate fuel supply path, and the ratio of wherein said maximum volume V2 and described minimum volume V1 meets following relation: 35%≤V1/V2≤85%.
According to the low backpressure rotary compressor of the embodiment of the present invention, following relation is met: 35%≤V1/V2≤85% by the ratio of the maximum volume V2 and minimum volume V1 that make slide plate chamber, therefore the pressure surge in slide plate chamber can not be excessive or too small, what can ensure slide plate and piston is close to sealing, thus while meeting the stressed needs of slide plate preferably, realize good compressor performance.
Preferably, the ratio of described maximum volume V2 and described minimum volume V1 meets following relation: 50%≤V1/V2≤70%.
In some embodiments of the invention, the vertical distance arriving the diapire in described slide plate chamber bottom of described oil supply hole is d, and the height of corresponding described cylinder is H, wherein 0≤d≤0.8H.
Preferably, the ratio of the area S3 of described oil supply hole and the minimum volume V1 in described slide plate chamber meets following relation: 0.1≤S3/V1≤10.5.
Further preferably, the ratio of the area S3 of described oil supply hole and the minimum volume V1 in described slide plate chamber meets following relation: 2≤S3/V1≤6.5.
According to some embodiments of the present invention, the area of the entrance of described fuel supply path is S1, and the minimum flow area of described fuel supply path is S2, and described S1, S2 and S3 meet following relation: S2≤S1, S2≤S3.
In some embodiments of the invention, described oil supply hole is arranged on the top in described slide plate chamber, and the ratio of the area S3 of described oil supply hole and the minimum volume V1 in described slide plate chamber meets following relation: S3/V1 >=4.5.
According to a particular embodiment of the invention, described oil separator is arranged on outside described housing and/or is located in described compressing mechanism.
In specific embodiments more of the present invention, described cylinder assembly comprises upper cylinder, lower cylinder and central diaphragm, described central diaphragm is located between described upper cylinder and described lower cylinder, and the slide plate chamber of described upper cylinder is communicated with described oil sump respectively with the slide plate chamber of described lower cylinder.
Further, the slide plate chamber of described upper cylinder is communicated with by the middle fuel supply path running through described central diaphragm with the slide plate chamber of described lower cylinder.
Preferably, the opening area being positioned at the slide plate chamber of described upper cylinder of described middle fuel supply path is S4, and the opening area being positioned at the slide plate chamber of described lower cylinder of described middle fuel supply path is S5, described S4 >=S5.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of low according to an embodiment of the invention backpressure rotary compressor, and wherein compressor is single cylinder compressor;
Fig. 2 is the schematic diagram according to the slide plate fuel supply path on the supplementary bearing of the embodiment of the present invention;
Fig. 3 is the cooperation schematic diagram of cylinder, slide plate and piston according to the embodiment of the present invention, and wherein the internal capacity in slide plate chamber is in minimum volume state;
Fig. 4 is the cooperation schematic diagram of cylinder, slide plate and piston according to the embodiment of the present invention, and wherein the internal capacity in slide plate chamber is in maximum volume state;
Fig. 5 is the schematic diagram of low in accordance with another embodiment of the present invention backpressure rotary compressor, and wherein compressor is single cylinder compressor;
Fig. 6 is the schematic diagram of low according to an embodiment of the invention backpressure rotary compressor, and wherein compressor is duplex cylinder compressor;
Fig. 7 is the schematic diagram of low in accordance with another embodiment of the present invention backpressure rotary compressor, and wherein compressor is duplex cylinder compressor;
Fig. 8 is the schematic diagram of the low backpressure rotary compressor according to another embodiment of the present invention, and wherein compressor is duplex cylinder compressor;
Fig. 9 is the schematic diagram of the low backpressure rotary compressor according to another embodiment of the present invention, and wherein compressor is duplex cylinder compressor;
Figure 10 is slide plate chamber volume-variation plotted curve;
Figure 11 is slide plate cavity pressure fluctuation tendency schematic diagram;
Figure 12 is the stressed schematic diagram of bent axle;
Figure 13 is according to the maximum volume V2 in the slide plate chamber of the embodiment of the present invention and the relation schematic diagram between the ratio of minimum volume V1 and the Energy Efficiency Ratio of compressor.
Reference character:
100 is low backpressure rotary compressor, and 1 is enclosure interior space, and 2 is slide plate chamber, 3 is slide plate fuel supply path, and 4 is vane slot, and 5 is oil sump, 6 is exhaust port, and 10 is housing, and 11 is main bearing, 12 is cylinder, and 13 is piston, and 14 is slide plate, 15 is supplementary bearing, and 16 is bent axle, and 17 is cover plate, 18 is oil separator, and 21 is stator, and 22 is rotor
H is cylinder height, and d is oil supply hole distance slide plate chamber, slide plate chamber distance from bottom, and P is exhaust pressure, and P1 is slide plate chamber pressure minimum, and P2 is slide plate chamber pressure maximum, and V1 is slide plate chamber minimum volume, and V2 is slide plate chamber maximum volume.
Embodiment
Be described below in detail embodiments of the invention, the example of described embodiment is shown in the drawings.Be exemplary below by the embodiment be described with reference to the drawings, be intended to for explaining the present invention, and can not limitation of the present invention be interpreted as.
In describing the invention, it will be appreciated that, term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", D score, " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " top ", " end " " interior ", " outward ", " clockwise ", " counterclockwise ", " axis ", " radial direction ", orientation or the position relationship of the instruction such as " circumference " are based on orientation shown in the drawings or position relationship, only the present invention for convenience of description and simplified characterization, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore limitation of the present invention can not be interpreted as.
In addition, term " first ", " second " only for describing object, and can not be interpreted as instruction or hint relative importance or imply the quantity indicating indicated technical characteristics.Thus, be limited with " first ", the feature of " second " can express or impliedly comprise at least one this feature.In describing the invention, the implication of " multiple " is at least two, such as two, three etc., unless otherwise expressly limited specifically.
In the present invention, unless otherwise clearly defined and limited, the term such as term " installation ", " being connected ", " connection ", " fixing " should be interpreted broadly, and such as, can be fixedly connected with, also can be removably connect, or integral; Can be mechanical connection, also can be electrical connection or each other can communication; Can be directly be connected, also indirectly can be connected by intermediary, can be the connection of two element internals or the interaction relationship of two elements, unless otherwise clear and definite restriction.For the ordinary skill in the art, above-mentioned term concrete meaning in the present invention can be understood as the case may be.
Describe the low backpressure rotary compressor 100 according to the embodiment of the present invention in detail below with reference to Fig. 1-Fig. 9, wherein low backpressure rotary compressor 100 can be single cylinder compressor also can be duplex cylinder compressor.
As shown in Fig. 1-Fig. 9, according to the low backpressure rotary compressor 100 of the embodiment of the present invention, comprising: housing 10, compressing mechanism, oil separator 18 and oil sump 5.Its middle shell 10 is provided with relief opening 6 and gas returning port (scheming not shown).
Compressing mechanism is located in housing 10, compressing mechanism comprises cylinder assembly, piston 13, slide plate 14, main bearing 11 and supplementary bearing 15, main bearing 11 and supplementary bearing 15 are located in the both ends of the surface of cylinder assembly respectively, cylinder assembly comprises at least one cylinder 12, a piston 13 is provided with in each cylinder 12, the tip of slide plate 14 is only against on the periphery wall of piston 13, cylinder 12 also has slide plate chamber 2, slide plate chamber 2 has oil supply hole, when slide plate 14 moves back and forth, the tail end of slide plate 14 stretches into or stretches out slide plate chamber 2 and changes between maximum volume V2 and minimum volume V1 to make the internal capacity in slide plate chamber 2.
Oil separator 18 is for carrying out Oil-gas Separation to the refrigerant of discharging from cylinder 12.The lubricant oil that oil sump 5 is separated for holding oil separator 18, because the refrigerant of discharging from cylinder 12 is high pressure refrigerant, it can thus be appreciated that oil sump 5 is in hyperbaric environment.
Oil sump 5 is communicated with oil supply hole by slide plate fuel supply path 3, and wherein the ratio of maximum volume V2 and minimum volume V1 meets following relation: 35%≤V1/V2≤85%.Wherein because slide plate chamber 2 is communicated with oil sump 5, it can thus be appreciated that slide plate chamber 2 is in hyperbaric environment, thus the tip of slide plate 14 can be made only to be against on the periphery wall of piston 13.
Be understandable that, low backpressure rotary compressor 100 also comprises motor, element such as bent axle 16 grade, motor comprises stator 21 and rotor 22, stator 21 is fixed on the inwall of housing 10, be enclosed within rotor 22 outside stator 21, be enclosed within outside rotor 22 on bent axle 16 and rotate with driving crank 16, be enclosed within outside the piston 13 of each cylinder 12 on the eccentric part of bent axle 16, in the vane slot 4 that slide plate 14 is located at cylinder 12 and the tip of slide plate 14 be only against piston 13 periphery wall on to be separated into air aspiration cavity and compression chamber by cylinder 12, wherein bent axle 16 drives piston 13 to do eccentric motion in corresponding cylinder 12, in the process of piston 13 eccentric rotary, slide plate 14 moves reciprocatingly in vane slot 4, during slide plate 14 to-and-fro motion, the tail end of slide plate 14 extend in slide plate chamber 2 or stretches out slide plate chamber 2, thus the internal capacity in slide plate chamber 2 is also along with the to-and-fro motion generating period of slide plate 14 changes.
Figure 10 shows that in compressor operation process, along with the to-and-fro motion of slide plate 14, the volume-variation situation schematic diagram in slide plate chamber 2.As shown in Figure 10, slide plate chamber 2 volume changes within the scope of V1 ~ V2, and wherein, abscissa is the angle of swing of piston 13 relative to cylinder axis.As shown in Figure 3, when slide plate 14 is accommodated in slide plate chamber 2 completely, now bent axle 16 angle of swing is 0 degree, the volume in slide plate chamber 2 is minimum, minimum volume is V1, and as shown in Figure 4, when slide plate 14 stretch out slide plate chamber 2 the longest time, now bent axle 16 angle of swing is 180 degree, and the volume in slide plate chamber 2 is maximum, and maximum volume is V2, after bent axle 16 revolves and turns around, when slide plate 14 is accommodated in slide plate chamber 2 again completely, now bent axle 16 angle of swing is 360 degree (radian 2 π), and the volume in slide plate chamber 2 becomes minimum volume V1 again.Shown in Figure 10 is pressure period of change ideally, in the compressor of reality, due to the process influence that the pressure loss and pressure transmit, may there is delay in pressure surge and abscissa bent axle 16 angle of swing, but periodically fluctuation change to attributes is constant.
According to the working principle of rotary compressor, as shown in Figure 3 and Figure 4, if the radius of piston 13 eccentric rotary is e, then the reciprocating range of slide plate 14 is 2e, if cylinder height is H, slide plate 14 thickness is T, then approximate have:
V2＝V1+2e*H*T
Along with the to-and-fro motion of slide plate 14, consider that slide plate 14 is minimum with the leakage-gap of cylinder fitting surface, therefore, slide plate chamber 2 is except being communicated with slide plate fuel supply path 3, and its internal capacity can be assumed to an airtight space.Like this, pressure in slide plate chamber 2 can produce fluctuation along with the change of slide plate chamber 2 volume, if the pressure of the entrance oil sump 5 of slide plate fuel supply path 3 is P, along with the volume-variation in slide plate chamber 2, pressure in slide plate chamber 2 can existence range be the pressure surge of P1 ~ P2, and the High-back-pressure rotary compressor that this point and traditional slide plate chamber open at enclosure interior space is diverse.In general, the outlet being positioned at slide plate chamber 2 of the slide plate fuel supply path 3 in slide plate chamber 2 and the size of oil supply hole can produce certain impact to this pressure surge, but generally speaking, the trend of slide plate chamber 2 internal pressure fluctuation as shown in figure 11.According to Figure 11, generally, along with the to-and-fro motion of slide plate 14, when slide plate chamber 2 volume is minimum, its pressure reaches maximum P2, and when slide plate chamber 2 volume is maximum, its pressure reaches minimum value P1, relative to the charge oil pressure P in slide plate chamber 2, there is relation P1 < P < P2.Same, the fluctuation of pressure and the angle of swing of bent axle 16 also may be delayed, and its fluctuation is mainly subject to the impact of volume-variation.
In rotary compressor operation process, rotate under the drive of the moment of rotation that bent axle 16 inputs at motor, and bent axle 16 also exists resisting moment M in operation process, resisting moment M is made up of several part, as shown in figure 12, comprising:
M＝Mg+Mn+Mc+Mj
Wherein:
Mg: the resisting moment that compressed gas forces produces
Mn: slide plate 14 tip acts on the resisting moment that the power Fn on piston 13 external diameter is formed
Mc: the friction torque between rolling piston 13 and eccentric crankshaft 16
Mj: the resisting moment that bent axle 16 produces with upper, supplementary bearing 15
In these resisting moment, Mn is the resisting moment that slide plate 14 tip acts on the power Fn formation on piston 13 external diameter, and in low backpressure rotary compressor, by known to the force analysis of slide plate 14, the gas force Fc of slide plate 14 afterbody affects slide plate 14 tip to act on one of the key factor of the power Fn on piston 13 external diameter, the gas force Fc of slide plate 14 afterbody is larger, and the power Fn that slide plate 14 tip acts on piston 13 external diameter is larger.And the gas force Fc of slide plate 14 afterbody obtains like this:
Fc＝Pc*Sc
Wherein,
Pc: the gas pressure of slide plate 14 afterbody
Sc: the lifting surface area of slide plate 14 afterbody
In low backpressure rotary compressor 100, because slide plate 14 afterbody is arranged in slide plate chamber 2, when structure is certain, the gas force Fc of slide plate 14 afterbody decides primarily of the pressure P c in slide plate chamber 2.According to analysis above, the gas pressure in slide plate chamber 2 fluctuates within the scope of P1 ~ P2, and therefore, the gas force Fc of slide plate 14 afterbody also exists fluctuation.
In rotary compressor operation process, the power of slide plate 14 clamping piston 13 will remain in suitable scope, resistance when avoiding excessive excessive or too small time occur leak and collision, therefore, for the gas pressure of slide plate 14 afterbody, the scope that also existence one is suitable.
Because the scope of the gas pressure in slide plate chamber 2 and the gas pressure of slide plate 14 afterbody mainly affects by the volume-variation scope V1 in charge oil pressure P and slide plate chamber 2 and V2, therefore, can by the gas pressure range regulating P and V1, V2 carry out condition slide plate 14 afterbody.
Under steady running condition, charge oil pressure P is certain, therefore, pressure surge can be appeared within the scope of suitable P1 ~ P2 as much as possible by the design volume-variation scope V1 in slide plate chamber 2 and the relation of V2.Figure 13 shows the runnability of low backpressure rotary compressor 100 and the volume-variation scope V1 in COP and slide plate chamber 2 and the ratio of V2 and the relation of V1/V2, is described as follows:
In compressor operation process, if the internal capacity V in slide plate chamber 2 has periodically variable scope V1 ~ V2 along with the to-and-fro motion of slide plate 14, wherein, V1 is the minimum volume in slide plate chamber 2, V2 is the maximum volume in slide plate chamber 2, then can pass through structural design, the relation of V1 and V2 is set to:
0.25%≤V1/V2≤95%; can ensure under most situation operating conditionss of low backpressure rotary compressor 100; ensure that slide plate 14 tip acts on the power of piston 13 external diameter; to guarantee that slide plate 14 and piston 13 can fit tightly; there will not be separation, thus ensure performance and the reliability of compressor.The relation of the Energy Efficiency Ratio (COP) of V1/V2 and housing 10 low-pressure rotary compressor is as shown in figure 13:
If when arranging 35%≤V1/V2≤85%, the power Fn that suitable slide plate 14 tip acts on piston 13 external diameter can be obtained, to ensure under most of operating mode, compressor can obtain better performance, and can ensure slide plate 14 and piston 13 be close to sealing, this is because, when the maximum volume in this slide plate chamber 2 and minimum volume than, the pressure surge in slide plate chamber 2 can not be excessive or too small, with reference in Figure 11, namely the amplitude of the relative P of P2 with P1 in the reasonable scope, thus while meeting the stressed needs of slide plate 14 preferably, realize good compressor performance.
According to the result in Figure 13, when the scope of V1/V2 is 50%≤V1/V2≤70%, the performance requirement of compressor can be better met.Therefore in a preferred embodiment of the invention, slide plate chamber 2 is designed so that the ratio of maximum volume V2 and minimum volume V1 meets following relation: 50%≤V1/V2≤70%.
In fig. 13, when V1/V2 is too small, as V1/V2 < 20%, because the existence in hole dodged by slide plate chamber 2 processing technology and slide plate 14 spring, be difficult to from a structural point realize, therefore, in Figure 13, be represented by dotted lines possible situation.And when V1/V2 is excessive, the volume-variation due to slide plate chamber 2 is little causes the pressure surge in slide plate chamber 2 little, the fuel feeding difficulty in slide plate chamber 2 may be caused, bring the deterioration of greasy property, cause the COP of compressor to decline.
Therefore, to sum up analyze known, according to the low backpressure rotary compressor 100 of the embodiment of the present invention, following relation is met: 35%≤V1/V2≤85% by the ratio of the maximum volume V2 and minimum volume V1 that make slide plate chamber 2, therefore the pressure surge in slide plate chamber 2 can not be excessive or too small, what can ensure slide plate 14 and piston 13 is close to sealing, thus while meeting the stressed needs of slide plate 14 preferably, realizes good compressor performance.
Wherein, in the volume-variation process of slide plate chamber 2, in slide plate chamber 2, trapped fuel situation also can have influence on the pressure surge in slide plate chamber 2.This is because lubricant oil is liquid; belong to incompressible product; if the trapped fuel amount in slide plate chamber 2 is too much; during slide plate 14 to-and-fro motion; the resistance of compression lubricant oil can be greatly; thus have influence on performance and the wearing and tearing of compressor, even cause under extreme case in compressor operation process due to the excessive and stuck shutdown of resistance.
In order to avoid the generation of this situation, the lubricant oil in slide plate chamber 2 must be made can the buffering suitable according to actual conditions to reduce when slide plate chamber 2 volume diminishes, in the present invention, can be realized by following scheme:
The first: be also the most reliable, exactly the oil supply hole in slide plate chamber 2 is arranged on the bottom in slide plate chamber 2, the distance d that namely oil supply hole arrives bottom slide plate chamber 2 is bottom set to d=0.
The second: middle part oil supply hole being arranged on slide plate chamber 2, mainly consider that the suitable trapped fuel in slide plate chamber 2 can improve the lubrication of slide plate 14 and the sealing of fitting surface, when slide plate 14 to-and-fro motion, when slide plate chamber 2 volume reduces, lubricant oil in slide plate chamber 2 can part retain, and can not be pushed back in oil supply hole completely, therefore, here, the open height d designing the oil supply hole in slide plate chamber 2 is 0 < d≤0.8*H.
In brief, oil supply hole can be arranged on bottom or the middle part in slide plate chamber 2, and the vertical distance arriving the diapire in slide plate chamber 2 bottom of oil supply hole is d, and the height of corresponding cylinder 12 is H, wherein 0≤d≤0.8H.
In addition, the trapped fuel in slide plate chamber 2 can realize reclaiming buffering by oil supply hole, thus avoid slide plate 14 to compress Performance And Reliability problem that lubricant oil brings compressor.Therefore, the size design of oil supply hole also can bring impact to the recovery buffering of trapped fuel.
The opening area design of rational oil supply hole is relevant with the volume in slide plate chamber 2, and by the area of slide plate chamber 2 oil supply hole reasonable in design, the trapped fuel realizing slide plate chamber 2 oil supply hole and slide plate fuel supply path 3 reclaims buffer function.When oil supply hole being arranged on to bottom or the middle part in slide plate chamber 2, generally, if the area of oil supply hole is S3 (unit: mm 2), the minimum volume V1 unit when itself and slide plate chamber 2: cm 3) numeric ratio when being 0.1≤S3/V1≤10.5, the pressure surge in the slide plate chamber 2 of low backpressure rotary compressor 100 will be in acceptable scope, can ensure the reliable and stable running of compressor.
Further, the area S3 (unit: mm of oil supply hole 2) with the minimum volume V1 (unit: cm in slide plate chamber 2 3) numeric ratio can be designed to 2≤S3/V1≤6.5.
Finally, if when the oil supply hole in slide plate chamber 2 is arranged on the top in slide plate chamber 2, just need to ensure that oil supply hole has good oil return performance, at this moment, the area S3 (unit: mm of oil supply hole can be designed 2) with the minimum volume V1 (unit: cm in slide plate chamber 2 3) numeric ratio be: S3/V1>=4.5, make the minimum volume comparing slide plate chamber 2, and the area of oil supply hole is enough large.
In addition, for slide plate fuel supply path 3, as shown in Figure 2, if the inlet area of slide plate fuel supply path 3 is S1, the minimum flow area of slide plate fuel supply path 3 is S2, when the outlet of slide plate fuel supply path 3 and the area of oil supply hole are S3, when being designed to import and exporting bigger, easierly can realize lubricant oil input and output fuel supply path, thus ensure that slide plate fuel supply path 3 is to slide plate chamber 2 oil mass provided and the effect of reclaiming buffering.Namely, in design, require that the area relationship at each position of slide plate fuel supply path 3 is: S2≤S1, and S2≤S3.When equal sign is set up, processing and the manufacture of slide plate fuel supply path 3 can be simplified.
In a particular embodiment of the present invention, oil separator 18 can be arranged on outside housing 10 and/or be located in compressing mechanism.Specifically, the facilities of oil separator 18 is divided into following several situation:
The first situation is, as shown in figure 5 and figure 7, when low backpressure rotary compressor 100 be single cylinder compressor or duplex cylinder compressor time, oil separator 18 is one and is arranged on outside housing 10, oil sump 5 is positioned at the bottom of oil separator 18, oil separator 18 is communicated with the exhaust port 6 of compressor, and each slide plate chamber 2 is communicated with oil sump 5.
The second situation is: low backpressure rotary compressor 100 is single cylinder compressor, and as shown in Figure 1, oil supply hole is positioned at the bottom in slide plate chamber 2, and oil separator 18 is arranged in the exhaust cavity that supplementary bearing 15 and cover plate 17 limit.
The third situation is: low backpressure rotary compressor 100 is single cylinder compressor, and oil supply hole is positioned at the top in slide plate chamber 2, then oil separator 18 is arranged in the exhaust cavity in main bearing 11.
4th kind of situation is: low backpressure rotary compressor 100 is duplex cylinder compressor, then main bearing 11 and supplementary bearing 15 are respectively equipped with oil separator 18 and oil sump 5.
5th kind of situation is: low backpressure rotary compressor 100 is duplex cylinder compressor, first oil sump of the lubricant oil being provided with first oil separator in the exhaust cavity of main bearing or supplementary bearing and separate for access first oil separator, housing 10 is outer is also provided with second oil separator, the bottom of the second oil separator is provided with the second oil sump, and the slide plate chamber of two cylinders is communicated with the second oil sump with first oil sump respectively.
The low backpressure rotary compressor 100 according to the several different embodiment of the present invention is described in detail below with reference to Fig. 1, Fig. 5-Fig. 9.
Embodiment 1:
As shown in Figure 1, according to the low backpressure rotary compressor 100 of the embodiment of the present invention, comprising: housing 10, motor and compressing mechanism.Limit the inner space 1 be communicated with intakeport in housing 10, motor is located at the top of inner space 1, and motor is made up of stator 21 and rotor 22, and wherein, rotor 22 is connected with bent axle 16, and driving crank 16 rotates.
Compressing mechanism comprises: cylinder 12, be arranged on piston 13 in cylinder 12 and slide plate 14, driven plunger 13 are made the bent axle 16 of eccentric rotary and support main bearing 11 and the supplementary bearing 15 of bent axle 16.
In compressor operation process, slide plate 14 is reciprocating along the vane slot 4 be arranged on cylinder 12, and the tip of slide plate 14 and the external diameter of piston 13 fit tightly and form compression chamber.
Supplementary bearing 15 bottom is provided with exhaust cavity, and this exhaust cavity coordinates by supplementary bearing 15 and cover plate 17 chamber sealed with enclosure interior space 1 pressure formed, and the pressure wherein in exhaust cavity is the exhaust pressure P of compressing mechanism.Oil separator 18 is arranged in exhaust cavity, bottom exhaust cavity, is provided with oil sump 5, is used for collecting the lubricant oil that in exhaust cavity, oil separator 18 is separated.
At the afterbody of slide plate 14, be positioned at the outer rim position of cylinder 12, be provided with the slide plate chamber 2 with housing 10 inner space 1 pressure sealed separation, this slide plate chamber 2 has internal capacity V, and, due to slide plate chamber 2 and enclosure interior space 1 pressure sealed separation, therefore, along with the to-and-fro motion of slide plate 14, the size of the inner space V in slide plate chamber 2 is also along with change, and excursion is V1 ~ V2, wherein, V1 is the minimum volume in slide plate 14 slide plate chamber 2 when receiving completely to vane slot 4, V2 then for slide plate 14 stretch out vane slot 4 the longest time slide plate chamber 2 maximum volume.
Wherein, the minimum volume V1 of slide plate chamber volume V and maximum volume V2 possesses following relation: 35%≤V1/V2≤85%.
Further, more suitably the scope of V1/V2 can be contracted to: 50%≤V1/V2≤70%.
In addition, as shown in Figure 1, low backpressure rotary compressor 100 is also provided with slide plate fuel supply path 3, the entrance of this slide plate fuel supply path 3 is communicated with the oil sump 5 in exhaust cavity, slide plate fuel supply path 3 is arranged on supplementary bearing 15, in the present embodiment, the outlet of fuel supply path 3 and slide plate chamber oil supply hole are arranged on the bottom in slide plate chamber 2, as shown in fig. 1.As shown in Figure 2, fuel supply path 3 inlet area is S1, and fuel supply path 3 minimum sectional area is S2, and the area of outlet and oil supply hole is S3.
Wherein, the outlet of slide plate fuel supply path 3 and the area S3 (unit: mm of oil supply hole 2) with the minimum volume V1 (unit: cm in slide plate chamber 2 3) numeric ratio be: 0.1≤S3/V1≤10.5.
Further, the scope of S3/V1 can be contracted to: 2≤S3/V1≤6.5.
Further, the entrance of this slide plate fuel supply path 3, the minimum sectional area S2 of fuel supply path 3, the area S3 relation of outlet are set to: S2≤S1, and S2≤S3.
Embodiment 2:
As shown in Figure 5, in this embodiment, the oil separator 18 of low backpressure rotary compressor 100 is arranged on the outside of housing 10, and this oil separator 18 is communicated with exhaust port 6.Oil sump 5 is arranged on the bottom of oil separator 18, the entrance of slide plate fuel supply path 3 is communicated with the oil sump 5 be arranged in oil separator 18, slide plate fuel supply path 3 is the fuel supply line being communicated with oil sump 5 and slide plate chamber 2, and the outlet of slide plate fuel supply path 3 and the oil supply hole in slide plate chamber 2 are positioned at the middle part in slide plate chamber 2.
Wherein, the distance of the bottom in oil supply hole distance slide plate chamber 2 is d, and the height in slide plate chamber 2 is H, has:
0＜d≤0.8*H
All the other are identical with embodiment 1, repeat no more.
Embodiment 3:
As shown in figures 7 and 9, in the present embodiment, be that compressing mechanism has upper and lower two cylinders with the difference of embodiment 1 and embodiment 2, namely cylinder assembly comprises upper cylinder 12a, lower cylinder 12b and central diaphragm, central diaphragm is located between upper cylinder 12a and lower cylinder 12b, correspondingly, slide plate chamber 2 also comprises slide plate chamber 2a and lower slide plate chamber 2b, the slide plate chamber 2a of upper cylinder 12a is communicated with oil sump respectively with the slide plate chamber 2b of lower cylinder 12b, and, the fuel supply path 3 in slide plate chamber also comprises fuel supply path 3a and lower fuel supply path 3b ...
That is, in the present embodiment, upper cylinder 12a and lower cylinder 12b is analyzed with the method for individual cylinder accordingly respectively, the volume V in the slide plate chamber of two cylinders, the area S3 of pressure P and oil supply hole and the slide plate cavity configuration correspondence analysis of respective cylinder, and after the parameter that upper cylinder 12a is corresponding, add a represent, as 12a, V1a, V2a, S3a etc., and add b to represent after the parameter that lower cylinder 12b is corresponding, as 12b, V2b, S3b etc.
Therefore, in the present embodiment, the volume scope in upper cylinder slide plate chamber is V1a ~ V2a, range of pressure fluctuations is P1a ~ P2a, the entrance of upper slide plate fuel supply path 3a, the minimum cross-sectional area of fuel supply path and the area of outlet are respectively S1a, S2a and S3a, and oil supply hole is da apart from the distance bottom upper slide plate chamber, the height of upper cylinder is Ha, and these parameters also possess the corresponding parameters relationship described in embodiment 1:
35%≤V1a/V2a≤85%, further optimum choice is 50%≤V1a/V2a≤70%;
0.1≤S3a/V1a≤10.5, further: 2≤S3a/V1a≤6.5;
Further, S2a≤S1a, and S2a≤S3a.
Same, the requirement of the parameter of lower cylinder and relation also similar upper cylinder, has:
35%≤V1b/V2b≤85%, further optimum choice is 50%≤V1b/V2b≤70%;
0.1≤S3b/V1b≤10.5, further: 2≤S3b/V1b≤6.5;
Further, S2b≤S1b, and S2b≤S3b.
Wherein, as shown in Figure 7, oil separator 18 is arranged on outside housing 10, oil sump 5 is positioned at the bottom of oil separator 18, and the oil supply hole of upper cylinder slide plate chamber 2a is positioned at middle part, and the oil supply hole of lower cylinder slide plate chamber 2b is positioned at middle part, that is, the outlet of upper slide plate fuel supply path 3a is positioned at the middle part of upper cylinder slide plate chamber 2a, and the outlet of lower slide plate fuel supply path 3b is positioned at the middle part of lower cylinder slide plate chamber 2b, and upper slide plate fuel supply path 3a is communicated with oil sump 5 respectively with lower slide plate fuel supply path 3b.
As shown in Figure 9, oil sump is respectively equipped with in the exhaust cavity of main bearing 11 and supplementary bearing 15, the oil supply hole of upper cylinder slide plate chamber 2a is positioned at the middle part of slide plate chamber 2a, and upper slide plate fuel supply path 3 is to be communicated with the oil sump in main bearing 11 and lower end extend into the fuel supply line in the 2a of slide plate chamber.The oil supply hole of lower cylinder slide plate chamber 2b is positioned at the bottom of slide plate chamber 2b.
Embodiment 4:
As shown in Figure 8, oil supply hole in the slide plate chamber 2a of upper cylinder 12a is arranged at top, and the oil supply hole of lower slide plate chamber 2b is arranged on bottom or middle part, now, middle fuel supply path 3m is provided with between upper slide plate chamber 2a and lower slide plate chamber 2b, wherein the opening area of this middle fuel supply path 3m in upper slide plate chamber 2a is S4, and the opening area in lower slide plate chamber 2b is S5, has S4 >=S5.In other words, the slide plate chamber 2a of upper cylinder 12a is communicated with by the middle fuel supply path 3m running through central diaphragm with the slide plate chamber 2b of lower cylinder 12b.The opening area being positioned at the slide plate chamber 2a of upper cylinder 12a of middle fuel supply path 3m is S4, and the opening area being positioned at the slide plate chamber 2b of lower cylinder 12b of middle fuel supply path 3m is S5, S4 >=S5.
In the present embodiment, the relation of S4 and S5 can be divided into two-part in detail:
First, when the area of S5 arrange less time, consider the pressure buffer effect in the 2a of slide plate chamber, to be realized by middle fuel supply path 3m, therefore, require S4 > S5, to ensure that the oil in upper slide plate chamber 2a easierly can enter into middle fuel supply path 3m, now S5≤3.5mm 2;
The second, when the area of S5 arrange larger time, as S5 > 3.5mm 2time, can S4=S5 be set.
In the present embodiment simultaneously, the volume scope in upper cylinder slide plate chamber is V1a ~ V2a, range of pressure fluctuations is P1a ~ P2a, the entrance of upper slide plate fuel supply path 3a, the minimum cross-sectional area of fuel supply path and the area of outlet are respectively S1a, S2a and S3a, oil supply hole is da apart from the distance bottom upper slide plate chamber, and the height of upper cylinder is Ha, and these parameters also possess following corresponding parameters relationship:
35%≤V1a/V2a≤85%, further optimum choice is 50%≤V1a/V2a≤70%;
S3a/V1a≥4.5；
Further, S2a≤S1a, and S2a≤S3a.
Same, the requirement of the parameter of lower cylinder and relation also similar upper cylinder, has:
35%≤V1b/V2b≤85%, further optimum choice is 50%≤V1b/V2b≤70%;
0.1≤S3b/V1b≤10.5, further: 2≤S3b/V1b≤6.5;
Further, S2b≤S1b, and S2b≤S3b.
Embodiment 5:
As shown in Figure 6, the difference of the present embodiment and embodiment 4 is, does not arrange middle fuel supply path 3m, and, the outlet of the fuel supply path 3a of upper slide plate chamber 2a and the area S3a (unit: mm of oil supply hole 2) with the minimum volume V1a (unit: cm in slide plate chamber 3) numeric ratio be: S3a/V1a>=4.5.
All the other are identical with embodiment 4, repeat no more.
What needs were described is, the exemplary illustration of above-mentioned four kinds of specific embodiments just to low backpressure rotary compressor 100 according to the present invention, slide plate fuel supply path 3 is not limited to above-mentioned several with the annexation in slide plate chamber 2, such as when the slide plate chamber 2a of upper cylinder 12a is communicated with by middle fuel supply path 3m with the slide plate chamber 2b of lower cylinder 12b, oil separator 18 can be positioned at outside housing 10, the oil supply hole of the slide plate chamber 2a of upper cylinder 12a is positioned at middle part, and the oil supply hole of the slide plate chamber 2b of lower cylinder 12b is also positioned at middle part.
In the present invention, unless otherwise clearly defined and limited, fisrt feature second feature " on " or D score can be that the first and second features directly contact, or the first and second features are by intermediary mediate contact.And, fisrt feature second feature " on ", " top " and " above " but fisrt feature directly over second feature or oblique upper, or only represent that fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " below " and " below " can be fisrt feature immediately below second feature or tiltedly below, or only represent that fisrt feature level height is less than second feature.
In the description of this specification, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " example ", " concrete example " or " some examples " etc. means to describe in conjunction with this embodiment or example are contained at least one embodiment of the present invention or example.In this manual, to the schematic representation of above-mentioned term not must for be identical embodiment or example.And the specific features of description, structure, material or feature can combine in one or more embodiment in office or example in an appropriate manner.In addition, when not conflicting, the feature of the different embodiment described in this specification or example and different embodiment or example can carry out combining and combining by those skilled in the art.
Although illustrate and describe embodiments of the invention above, be understandable that, above-described embodiment is exemplary, can not be interpreted as limitation of the present invention, and those of ordinary skill in the art can change above-described embodiment within the scope of the invention, revises, replace and modification.

Claims (11)

1. a low backpressure rotary compressor, is characterized in that, comprising:
Housing, described housing is provided with relief opening and gas returning port;
Compressing mechanism, described compressing mechanism is located in described housing, described compressing mechanism comprises cylinder assembly, piston, slide plate, main bearing and supplementary bearing, described main bearing and described supplementary bearing are located in the both ends of the surface of described cylinder assembly respectively, described cylinder assembly comprises at least one cylinder, a described piston is provided with in each described cylinder, the tip of described slide plate is only against on the periphery wall of described piston, described cylinder also has slide plate chamber, described slide plate chamber has oil supply hole, when described slide plate moves back and forth, the tail end of described slide plate stretches into or stretches out described slide plate chamber and changes between maximum volume V2 and minimum volume V1 to make the internal capacity in described slide plate chamber,
For carrying out the oil separator of Oil-gas Separation to the refrigerant of discharging from described cylinder;
For holding the oil sump of the lubricant oil that described oil separator is separated, described oil sump is communicated with described oil supply hole by slide plate fuel supply path, and the ratio of wherein said maximum volume V2 and described minimum volume V1 meets following relation: 35%≤V1/V2≤85%.
2. low backpressure rotary compressor according to claim 1, is characterized in that, the ratio of described maximum volume V2 and described minimum volume V1 meets following relation: 50%≤V1/V2≤70%.
3. low backpressure rotary compressor according to claim 1, is characterized in that, the vertical distance arriving the diapire in described slide plate chamber bottom of described oil supply hole is d, and the height of corresponding described cylinder is H, wherein 0≤d≤0.8H.
4. low backpressure rotary compressor according to claim 3, is characterized in that, the ratio of the area S3 of described oil supply hole and the minimum volume V1 in described slide plate chamber meets following relation: 0.1≤S3/V1≤10.5.
5. low backpressure rotary compressor according to claim 4, is characterized in that, the ratio of the area S3 of described oil supply hole and the minimum volume V1 in described slide plate chamber meets following relation: 2≤S3/V1≤6.5.
6. low backpressure rotary compressor according to claim 1, is characterized in that, the area of the entrance of described fuel supply path is S1, and the minimum flow area of described fuel supply path is S2, and described S1, S2 and S3 meet following relation: S2≤S1, S2≤S3.
7. low backpressure rotary compressor according to claim 1, is characterized in that, described oil supply hole is arranged on the top in described slide plate chamber, and the ratio of the area S3 of described oil supply hole and the minimum volume V1 in described slide plate chamber meets following relation: S3/V1 >=4.5.
8. low backpressure rotary compressor according to claim 1, is characterized in that, described oil separator is arranged on outside described housing and/or is located in described compressing mechanism.
9. low backpressure rotary compressor according to claim 1, it is characterized in that, described cylinder assembly comprises upper cylinder, lower cylinder and central diaphragm, described central diaphragm is located between described upper cylinder and described lower cylinder, and the slide plate chamber of described upper cylinder is communicated with described oil sump respectively with the slide plate chamber of described lower cylinder.
10. low backpressure rotary compressor according to claim 9, is characterized in that, the slide plate chamber of described upper cylinder is communicated with by the middle fuel supply path running through described central diaphragm with the slide plate chamber of described lower cylinder.
11. low backpressure rotary compressor according to claim 10, it is characterized in that, the opening area being positioned at the slide plate chamber of described upper cylinder of described middle fuel supply path is S4, and the opening area being positioned at the slide plate chamber of described lower cylinder of described middle fuel supply path is S5, described S4 >=S5.
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CN104912808A (en) * 2015-06-25 2015-09-16 广东美芝制冷设备有限公司 Compressing mechanism and low-back-pressure rotation type compressor with same
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CN104912808A (en) * 2015-06-25 2015-09-16 广东美芝制冷设备有限公司 Compressing mechanism and low-back-pressure rotation type compressor with same
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