CN1940292A - Hermetic compressor - Google Patents
Hermetic compressor Download PDFInfo
- Publication number
- CN1940292A CN1940292A CNA2006101388113A CN200610138811A CN1940292A CN 1940292 A CN1940292 A CN 1940292A CN A2006101388113 A CNA2006101388113 A CN A2006101388113A CN 200610138811 A CN200610138811 A CN 200610138811A CN 1940292 A CN1940292 A CN 1940292A
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- China
- Prior art keywords
- exhaust
- closed compressor
- reed
- apical grafting
- discharge valve
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/1066—Valve plates
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F1/00—Springs
- F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
- F16F1/18—Leaf springs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K15/00—Check valves
- F16K15/14—Check valves with flexible valve members
- F16K15/16—Check valves with flexible valve members with tongue-shaped laminae
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/12—Kind or type gaseous, i.e. compressible
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S251/00—Valves and valve actuation
- Y10S251/902—Springs employed as valves
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S415/00—Rotary kinetic fluid motors or pumps
- Y10S415/915—Pump or portion thereof by casting or molding
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
- Y10S417/902—Hermetically sealed motor pump unit
Abstract
The present invention provides a hermetic compressor capable of improving the closing delay of discharge reed, inhibiting deterioration of freezing capability and improving compression efficiency. Stopper (127) contains abutment section (131) at a position that corresponds to arm section (130) so as to keep a clearance from arm section (130) of discharge reed (126). The structure above allows discharge reed (126) to have two-stage spring characteristics; discharge reed (126) exhibits a weaker springiness until arm section (130) abuts against abutment section (131), and then exhibits a stronger springiness after the abutment. Employing the discharge reed having the two-stage characteristics allows discharge valve unit (114) to easily open and quickly close without delay. Such structured hermetic compressor enhances energy efficiency, preventing degradation in refrigeration performance.
Description
Technical field
The present invention relates to a kind of closed compressor that is mainly used in fridge-freezer etc., more particularly, relate to the improvement that discharge valve apparatus is wherein done.
Background technique
In existing closed compressor, noise when reducing work, the discharge valve apparatus (example wherein can be opened flat 10-318146 with reference to the Japanese patent gazette spy) that can improve efficiency of energy utilization generally all is equipped with in the loss that produces when opening and closing for degree of reduction exhaust reed simultaneously.
With reference to the accompanying drawings above-mentioned existing closed compressor is described.
Figure 13 is the sectional view of existing closed compressor, Figure 14 is the plan view of existing closed compressor, Figure 15 is the discharge valve apparatus exploded view of existing closed compressor, Figure 16 is the discharge valve apparatus side cross-sectional, view of existing closed compressor, and Figure 17 is the discharge valve apparatus spring performance figure of existing closed compressor.
In Figure 13, Figure 14, Figure 15, Figure 16 and Figure 17, seal casinghousing 1 is provided with outlet pipe 2 and the sucking pipe 3 that connects with the cooling system (not shown), and the bottom has stockpiled refrigeration oil 4.In addition, also be provided with the motor drive mechanism that constitutes by stator 5 and rotor 67 in the seal casinghousing 1 and by its compressor driven structure 8 in addition, inside is full of refrigerant 9.
Below the main composition parts in the compressing mechanism 8 are described.
Comprise on the cylinder 10 and roughly be pressing chamber 11 cylindraceous and axis body support unit 12.Pressing chamber 11 is stopped up by valve plate 13, and a side opposite with cylinder 10 in the valve plate 13 is provided with discharge valve apparatus 14.Valve plate 13 is covered by cylinder head 15.
Air suction silencer 16 is that tail pipe 17 and silence space (not shown) constitute by the refrigerant gas suction passage that is provided with opening in seal casinghousing 1, is connected in the other end of air suction silencer 16 and the pressing chamber 11.
Bent axle 18 has main shaft portion 19 and eccentric part 20, carries out axially support by the axis body support unit 12 that is located on the cylinder 10, also is pressed into simultaneously, is fixed in the rotor 6.Piston 21 is inserted in the cylinder 10 in the mode that can reciprocatingly slide freely, connects by between connecting rod 22 and the eccentric part 20 simultaneously.
Below discharge valve apparatus set in the compressing mechanism 8 14 is described.
A side opposite with cylinder 10 in the valve plate 13 is provided with valve seat 24, and this valve seat 24 is the shape that the exhaust port 23 that will be connected with cylinder 10 surrounds.
Be provided with the exhaust chamber 27 of packing into for discharge valve apparatus 14 in the cylinder head 15, and form one with the backstopping assembly 28 of the aperture that is used to limit exhaust reed 25.And valve plate 13, exhaust reed 25 and cylinder head 15 are put together with order stack recited above earlier, integrally are fixed to cylinder 10 1 sides by screw 29 then.
Below the operational circumstances in the closed compressor with above-mentioned formation is described.
When being energized in the motor drive mechanism 7, rotor 6 will rotate, and drive bent axle 18 rotations.Meanwhile, the off-centre of eccentric part 20 rotatablely moves and is delivered on the piston 21 by connecting rod 22, makes piston 21 reciprocating in pressing chamber 11.
Along with the to-and-fro motion of piston 21, the refrigerant 9 in the seal casinghousing 1 is drawn in the pressing chamber 11 from air suction silencer 16, simultaneously, 9 of low-pressure refrigerants from the cooling system (not shown) in sucking pipe 3 flow into seal casinghousing 1.The refrigerant 9 that is drawn in the pressing chamber 11 is compressed earlier along with the motion of piston 21, and the discharge valve apparatus on valve plate 13 14 is discharged in the exhaust chamber 27 in the cylinder head 15 then.The exhaust chamber 27 interior high pressure refrigerant gas 9 that are discharged to cylinder head 15 are discharged to the cooling system (not shown) from outlet pipe 2 at last.
At this moment, discharge valve apparatus 14 carries out the opening and closing operations of following regulation: when opening by opening exhaust reed 25, pressing chamber 11 inside are connected with exhaust chamber 27 in the cylinder head 15 by exhaust port 23; By closing exhaust reed 25, again pressing chamber 11 exhaust chamber 27 inside inner and cylinder head 15 are sealed.
But, in above-mentioned existing apparatus constitutes, can only obtain constant spring performance in the scope of exhaust reed 25 before pushing up backstopping assembly 28.
Here, the operation to discharge valve apparatus 14 is described in detail.
When the exhaust reed 25 in discharge valve apparatus 14 is opened because in the cylinder 10 and the pressure difference in the exhaust chamber 27 of cylinder head 15 very big, the switching part 26 of exhaust reed 25 by after compression high pressure refrigerant gas 9 jack-up, is withstood with backstopping assembly 28 earlier again.
In addition, when in the cylinder 10 and the pressure difference in the exhaust chamber 27 of cylinder head 15 when diminishing, 26 of the switching parts of exhaust reed 25 are left backstopping assembly 28 under the recuperability effect of resiliently deformable, again valve seat 24 is sealed.
That is, the spring performance of exhaust reed 25 as shown in Figure 17, in the scope before withstanding backstopping assembly 28, being does not have spring performance flex point, constant.Like this, if the spring performance of exhaust reed 25 is weakened, then in the scope before exhaust reed 25 pushes up backstopping assembly 28, can rely on the constant spring performance realization and the aperture of the corresponding exhaust reed 25 of gas flow, exhaust reed 25 is easy to open, and can reduce the overcompression phenomenon.But simultaneously, the speed when exhaust reed 25 is closed can produce and close delay phenomenon also with slack-off, and high-pressure refrigerant 9 can flow backward in the pressing chamber 11, causes the actual exhaust air volume of piston 21 to reduce, and refrigerating capacity also can descend.
On the other hand, if strengthen the spring performance of exhaust reed 25, situation will be conversely: exhaust reed 25 is closed easily, but the reed elastic force when opening also can become greatly, exists the problem that the overcompression phenomenon can increase.
Summary of the invention
The present invention is intended to solve the above-mentioned problems in the prior art, and its purpose is to provide a kind of being provided with not only to open easily and the exhaust reed that closing velocity is also fast, the closed compressor that energy utilization rate is also high.
In order to solve the above-mentioned problems in the prior art, backstopping assembly in the closed compressor of the present invention with the corresponding position of bracketed part on be provided with the apical grafting part that has specified gap with bracketed part, make exhaust reed push up spring performance grow again after the spring performance of top-joining part before dividing weakens, withstands, have the spring performance in two stages at bracketed part.
The technique effect that the present invention produces is as follows.Closed compressor of the present invention is owing to have the spring performance in two stages, so the discharge valve apparatus of can obtain a kind ofly opening easily, closing velocity is also fast, thereby can provide that a kind of overvoltage reduces, refrigerating capacity height, closed compressor that energy utilization rate is also high.
The specific embodiment of the invention is summarized as follows.Closed compressor described in the scheme 1 comprises: the cylinder that piston moves back and forth therein; The opening end of described cylinder is sealed, be provided with the valve plate of discharge valve apparatus simultaneously in a side opposite with cylinder; With the cylinder head that is provided with the exhaust chamber of packing into for described discharge valve apparatus.Wherein, described discharge valve apparatus comprises: be located on the described valve plate, with described cylinder in the exhaust port that is connected; Be formed on the valve seat in the outside of described exhaust port; Make by the leaf spring material, have and make the switching part that described exhaust port opens and closes and the exhaust reed of bracketed part; Backstopping assembly with the aperture that is used to limit described exhaust reed.Described backstopping assembly and the corresponding position of described bracketed part on be provided with and described bracketed part between have the apical grafting part of predetermined gap.Like this, because the spring performance of exhaust reed a little less than bracketed part pushes up the spring performance of top-joining part before dividing, after withstanding is strong, spring performance with two stages, so the discharge valve apparatus of can obtain a kind ofly opening easily, closing velocity is also fast, thereby can provide that a kind of overvoltage reduces, refrigerating capacity height, closed compressor that energy utilization rate is also high.
Invention described in the scheme 2 is, on the basis of the invention described in the scheme 1, described backstopping assembly also have with open and close the restricted part that has the gap bigger on the corresponding position of part than apical grafting part.Like this, partly withstand restricted part by the switching that makes exhaust reed, can the further motion of exhaust reed be limited, reduce the stress of exhaust reed, on the basis of the effect of the invention described in the scheme 1, can provide a kind of reliability higher closed compressor.
Invention described in the scheme 3 is that on the basis of the invention described in scheme 1 or the scheme 2, described exhaust reed and backstopping assembly are fixed on the valve plate.Like this, under the occasion of phenomenons such as generation liquid compression, though highdensity liquid refrigerant can add very big load on the switching part of exhaust reed, it is pressed tight on the apical grafting face of backstopping assembly, but owing to backstopping assembly is fixed on the valve plate, so the phenomenon that backstopping assembly can not come off.On the basis of the invention effect described in scheme 1 or the scheme 2, can provide a kind of reliability higher closed compressor.
Invention described in the scheme 4 is that on the basis of the invention described in scheme 1 or the scheme 2, described backstopping assembly is formed in the cylinder head.Like this, the height dimension of apical grafting part and restricted part determines directly that by the cylinder head mould it is stable that the height of exhaust reed and backstopping assembly can keep.On the basis of the effect of the invention described in scheme 1 or the scheme 2, can also reduce the deviation of efficiency of energy utilization, reduce the kind of parts, thereby can provide a kind of manufacturing efficiency high closed compressor.
Invention described in the scheme 5 is that on the basis of the invention described in scheme 1 or the scheme 2, the apical grafting face of described apical grafting part and restricted part is formed by solid lubricant.Like this, because the friction factor between the apical grafting face of exhaust reed and apical grafting part and restricted part has reduced, even rapid displacement takes place, also very suitable cunning between the surface, can not block, therefore, the abrasion that the Metal Contact when exhaust reed pushes up on the backstopping assembly causes can be inhibited, on the basis of the effect of scheme 1 or scheme 2, can also improve the high closed compressor of a kind of reliability.
Description of drawings
Fig. 1 is the sectional view of the closed compressor in the embodiments of the present invention 1,
Fig. 2 is the plan view of the closed compressor in this mode of execution,
Fig. 3 is the discharge valve apparatus exploded view of the closed compressor in this mode of execution,
Fig. 4 is in the side cross-sectional, view of opening procedure during mid-term for the discharge valve apparatus of the closed compressor in this mode of execution,
Fig. 5 is in the side cross-sectional, view of opening procedure during latter stage for the discharge valve apparatus of the closed compressor in this mode of execution,
Fig. 6 is the spring performance figure of the discharge valve apparatus of the closed compressor in this mode of execution,
Fig. 7 is the sectional view of the closed compressor in the embodiment of the present invention 2,
Fig. 8 is the plan view of the closed compressor in this mode of execution,
Fig. 9 is the discharge valve apparatus exploded view of the closed compressor in this mode of execution,
Figure 10 is in the side cross-sectional, view of opening procedure during mid-term for the discharge valve apparatus of the closed compressor in this mode of execution,
Figure 11 is in the side cross-sectional, view of opening procedure during latter stage for the discharge valve apparatus of the closed compressor in this mode of execution,
Figure 12 is the spring performance figure of the discharge valve apparatus of the closed compressor in this mode of execution,
Figure 13 is the sectional view of existing closed compressor,
Figure 14 is the plan view of existing closed compressor,
Figure 15 is the discharge valve apparatus exploded view of existing closed compressor,
Figure 16 is the side cross-sectional, view of the discharge valve apparatus of existing closed compressor,
Figure 17 is the spring performance figure of the discharge valve apparatus of existing closed compressor.
In the above-mentioned accompanying drawing, 110,210 is cylinder, and 113,213 is valve plate, 114,214 is discharge valve apparatus, and 115,215 is exhaust chamber, and 116,216 is cylinder head, 122,222 is piston, and 124,224 is exhaust port, and 125,225 is valve seat, 126,226 is exhaust reed, 127,227 is backstopping assembly, and 129,229 for opening and closing part, and 130,230 is bracketed part, 131,231 is the apical grafting part, and 132,232 is restricted part.
Embodiment
With reference to the accompanying drawings the specific embodiment of the present invention is described in detail.
(mode of execution 1)
At first, by Fig. 1 to Fig. 6 the closed compressor in the mode of execution 1 is specifically described.Wherein, Fig. 1 is the sectional view of the closed compressor in the embodiment of the present invention 1, Fig. 2 is the plan view of the closed compressor in this mode of execution, Fig. 3 is the discharge valve apparatus exploded view of the closed compressor in this mode of execution, Fig. 4 is in the side cross-sectional, view of opening procedure during mid-term for the discharge valve apparatus of the closed compressor in this mode of execution, Fig. 5 is in the side cross-sectional, view of opening procedure during latter stage for the discharge valve apparatus of the closed compressor in this mode of execution, and Fig. 6 is the spring performance figure of the discharge valve apparatus of the closed compressor in this mode of execution.
In Fig. 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5 and Fig. 6, seal casinghousing 101 is provided with and joining outlet pipe 102 of cooling system (not shown) and sucking pipe 103, and the bottom has stockpiled refrigeration oil 104.In addition, also be equipped with in the seal casinghousing 101 motor drive mechanism 107 that constitutes by stator 105 and rotor 106, and by motor drive mechanism 107 compressor driven structure 108 in addition, inside has been full of refrigerant 109.Refrigerant 109 preferably adopts the refrigerant of thinking in recent years outside the fluorine Lyons that can cause environmental problem, as R134a and natural refrigerant R600a etc.
Below the main composition in the compressing mechanism 108 partly is described.
Have main shaft portion 120 and eccentric part 121 in the bent axle 119, carry out axially support by the axis body support unit on the cylinder 110 112, and be pressed into, be fixed in the rotor 106.Piston 122 is inserted in the cylinder 110 in the mode that can back and forth slide freely, connects by between connecting rod 123 and the eccentric part 121 simultaneously.
Below the discharge valve apparatus in the compressing mechanism 108 114 is described.
A side opposite with cylinder 110 in the valve plate 113 is provided with valve seat 125, and valve seat 125 forms the shape that the exhaust port 124 that will be connected with cylinder 110 surrounds.
Have apical grafting part 131 and restricted part 132 in the backstopping assembly 127.The aperture of 131 pairs of exhaust reeds 126 of described apical grafting part limits, simultaneously with bracketed part 130 corresponding positions on have predetermined gap with bracketed part 130.Restricted part 132 is in and opens and closes on the part 129 corresponding positions, has the gap bigger than apical grafting part 131.
Below operational circumstances in the closed compressor with above-mentioned formation and effect thereof are described.
When being energized in the motor drive mechanism 107, rotor 106 will rotate, and drive bent axle 119 rotations.Simultaneously, the off-centre of eccentric part 121 rotatablely moves and is delivered on the piston 122 by connecting rod 123, makes piston 122 reciprocating in pressing chamber 111.
Along with the to-and-fro motion of piston 122, the refrigerant 109 in the seal casinghousing 101 is sucked in the pressing chamber 111 from air suction silencer 117.Meanwhile, low-pressure refrigerant 109 will be from the cooling system (not shown) in sucking pipe 103 flow into seal casinghousing 101.The refrigerant 109 that is sucked in the pressing chamber 111 is compressed earlier, is discharged in the exhaust chamber 115 through the discharge valve apparatus 114 on the valve plate 113 again.The high pressure refrigerant gas 109 that is discharged in the exhaust chamber 115 is discharged to the cooling system (not shown) from outlet pipe 102 at last.
At this moment, discharge valve apparatus 114 carry out under opening and closing operations: by exhaust reed 126 is opened, make in the pressing chamber 111 and in the cylinder head 116 to interconnect by exhaust port 124; By exhaust reed 126 is closed, make in the pressing chamber 111 and maintenance sealing in the cylinder head 116.
Here, exhaust reed 126 is opened earlier under the reaction force acts of high-pressure refrigerant 109 gases, pushes up then on the apical grafting part 131 in the backstopping assembly 127.Therefore, before exhaust reed 126 pushes up apical grafting part 131 in the backstopping assembly 127, can obtain not having spring performance flex point, constant.First spring constant by in reducing during this just can make elastic force weaken, and exhaust reed 126 is opened easily.
Then, after exhaust reed 126 pushes up on the apical grafting part 131 in the backstopping assembly 127, because exhaust reed 126 will be being that elastic bending further takes place fulcrum in the apical grafting of apical grafting part 131 part position, so second spring constant will be bigger than first spring constant.Consequently, after on the apical grafting part 131, can obtain very strong rebounding force from very strong spring force, when exhaust reed 126 enters shutoff stroke, this very strong rebounding force will be had an effect, thereby can accelerate the closing velocity of exhaust reed 126.
As mentioned above, by before the bracketed part 130 apical grafting parts 131 of exhaust reed 126, reducing elastic force, after withstanding, then strengthen elastic force, can obtain the spring performance in two stages, the discharge valve apparatus 114 of realize a kind ofly opening easily, closing velocity is also fast can reduce overcompression phenomenon, refrigerating capacity height, closed compressor that efficiency of energy utilization is also high thereby can provide a kind of.
In addition, though only show the example that is provided with an apical grafting part 131 in the present embodiment, but, a plurality of such apical grafting parts 131 also can be set, spring performance set for can possess suitable easy degree and the rebounding force opened according to the aperture of exhaust reed 126, provide a kind of overcompression still less, refrigerating capacity is higher, efficiency of energy utilization is also higher closed compressor.
After exhaust reed 126 pushes up apical grafting part 131 in the backstopping assembly 127,, will push up on the restricted part 132 if further open.Because restricted part 132 and near the apical grafting that takes place of the front end of exhaust reed 126 are so exhaust reed 126 almost no longer carries out further displacement.Therefore, the situation that the internal stress that produces because of the distortion of exhaust reed 126 increases will be suppressed, even under the very big condition of the degree of crook of situation, exhaust reed 126 such as liquid compression takes place or the refrigerant gas of high concentration compressed, can prevent that also the stress in the exhaust reed 126 from increasing sharp, thereby it is damaged to prevent that it from taking place, and improves the reliability of compressor.
In addition, under occasions such as generation liquid compression, though highdensity liquid refrigerant will add very big load on the switching part 129 of exhaust reed 126, it is pressed tight on the apical grafting face of backstopping assembly 127, but, because backstopping assembly 127 is fixed on the valve plate 113 by rivet 133, thus the situation that backstopping assembly 127 comes off can not take place, thus can realize a kind of closed compressor of high reliability.
In addition, when exhaust reed 126 pushes up on the apical grafting face in the backstopping assembly 127, though exhaust reed 126 can be impacted, but the apical grafting face on the backstopping assembly in the present embodiment 127 has been processed to circular shape, so the characteristic of discharge valve apparatus 114 and reliability can be designed to be affacted hardly the influence of the impact stress on the exhaust reed 126.
(mode of execution 2)
Fig. 7 is the sectional view of the closed compressor in the embodiment of the present invention 2, Fig. 8 is the plan view of the closed compressor in this mode of execution, Fig. 9 is the discharge valve apparatus exploded view of the closed compressor in this mode of execution, Figure 10 is in the side cross-sectional, view of opening procedure during mid-term for the discharge valve apparatus of the closed compressor in this mode of execution, Figure 11 is in the side cross-sectional, view of opening procedure during latter stage for the discharge valve apparatus of the closed compressor in this mode of execution, and Figure 12 is the spring performance figure of the discharge valve apparatus of the closed compressor in this mode of execution.
In Fig. 7, Fig. 8, Fig. 9, Figure 10, Figure 11 and Figure 12, seal casinghousing 201 is provided with and joining outlet pipe 202 of cooling system (not shown) and sucking pipe 203, and the bottom has stockpiled refrigeration oil 204.In addition, the motor drive mechanism 207 that is made of stator 205 and rotor 206 also is housed in the seal casinghousing 201, and carries out compressor driven structure 208 by it, the inside of seal casinghousing 201 is refrigerant 209 abrim.Refrigerant 209 preferably uses generation in recent years can cause refrigerant beyond fluorine Lyons of environmental problem, as R134a and natural refrigerant R600a etc.
Below the main composition in the compressing mechanism 208 is described.
Be provided with main shaft portion 220 and eccentric part 221 in the bent axle 219, carry out axially support by the axis body support unit on the cylinder 210 212, and be pressed into, be fixed in the rotor 206.Piston 222 is inserted in the cylinder 210 in the mode that can reciprocatingly slide freely, and by connecting between connecting rod 223 and the eccentric part 221.
Below the discharge valve apparatus 214 that is provided with in the compressing mechanism 208 is described.
A side opposite with cylinder 210 on the valve plate 213 is provided with valve seat 225, and this valve seat 225 is the shape that the exhaust port 224 that will be connected with cylinder 210 surrounds.
Backstopping assembly 227 is used to limit the aperture of exhaust reed 226, forms one with cylinder head 216.This backstopping assembly 227 is provided with apical grafting part 231 and restricted part 232.Apical grafting part 231 be positioned at bracketed part 230 corresponding positions on, and have predetermined gap between the bracketed part 230; Restricted part 232 is in and opens and closes on the part 229 corresponding positions, has the gap bigger than apical grafting part 231.
In addition, have face shield 233 on the apical grafting face of apical grafting part 231, restricted part 232, this face shield 233 but has anti-refrigerant, chemical stability, stable on heating solid lubricant such as tetrafluoroethylene and makes by not having viscosity.
During assembling, valve plate 213, exhaust reed 226, cylinder head 216 are put together with above-mentioned order stack earlier, are fixed on cylinder 210 1 sides by screw 234 then.
Below operational circumstances in the closed compressor with above-mentioned formation and effect are described.
When switching in the motor drive mechanism 207, rotor 206 rotates, and drives bent axle 219 rotations.At this moment, the off-centre of eccentric part 221 rotatablely moves and is delivered on the piston 222 by connecting rod 223, thereby makes piston 222 reciprocating in pressing chamber 211.
Along with the to-and-fro motion of piston 222, the refrigerant 209 in the seal casinghousing 201 are sucked in the pressing chamber 211 from air suction silencer 217, simultaneously, low-pressure refrigerant 209 from the cooling system (not shown) in sucking pipe 203 flow into seal casinghousing 201.The refrigerant 209 that is sucked in the pressing chamber 211 is compressed earlier, and the discharge valve apparatus on valve plate 213 214 is discharged in the cylinder head 216 again.High-pressure refrigerant 209 gases that are discharged in the exhaust chamber 215 are discharged to the cooling system (not shown) from outlet pipe 202 at last.
At this moment, discharge valve apparatus 214 carries out following opening and closing operations: by exhaust reed 226 is opened, make in the pressing chamber 211 and in the cylinder head 216 to be connected by exhaust port 224; By exhaust reed 226 is closed, make in the pressing chamber 211 and maintenance sealing in the cylinder head 216.
Here, under the reaction force of the gas of high-pressure refrigerant 209, exhaust reed 226 is opened earlier, and then pushes up on the apical grafting part 231 in the backstopping assembly 227.Therefore, in the scope before exhaust reed 226 withstands on the apical grafting part 231 in the backstopping assembly 227, can obtain not having spring performance flex point, constant.By reducing first spring constant in this scope, can reduce the power of spring, make to open to become easy.
Next, after exhaust reed 226 withstands apical grafting part 231 in the backstopping assembly 227, exhaust reed 226 will with and apical grafting part 231 between apical grafting part position be fulcrum generation elastic bending, so second spring constant during this is bigger than first spring constant.Consequently, on the apical grafting part 231 after, can obtain very strong rebounding force because of very strong acting force of the spring, when exhaust reed 226 enters shutoff stroke, this very strong rebounding force will have been given play to the effect of the closing velocity of accelerating exhaust reed 226.
As mentioned above, by before the bracketed part 230 apical grafting parts 231 of exhaust reed 226, weakening elastic force, after withstanding, strengthen elastic force, thereby can obtain the spring performance in two stages, the discharge valve apparatus 214 of realize a kind ofly opening easily, closing velocity is also fast.Like this, can provide a kind of and can reduce overcompression phenomenon, refrigerating capacity height, closed compressor that efficiency of energy utilization is also high.
In addition, though only show the example that is provided with an apical grafting part 231 in the present embodiment, but, a plurality of such apical grafting parts 231 also can be set, spring performance set for can possess suitable easy opening degree and reaction force according to the aperture of exhaust reed 226, provide a kind of overcompression still less, refrigerating capacity is higher, efficiency of energy utilization is also higher closed compressor.
After exhaust reed 226 pushes up apical grafting part 231 in the backstopping assembly 227,, will push up on the restricted part 232 if further open.Because restricted part 232 and near the apical grafting that takes place of the front end of exhaust reed 226 are so exhaust reed 226 almost no longer carries out further displacement.Therefore, the internal stress increase that produces because of the distortion of exhaust reed 226 will be suppressed, even under the very big situation of the degree of crook of situation, exhaust reed 226 such as liquid compression takes place or the refrigerant gas of high concentration compressed, can prevent that also the stress in the exhaust reed 226 from increasing sharp, thereby it is damaged to prevent that it from taking place, and improves the reliability of compressor.
In addition, backstopping assembly 227 and cylinder head 216 can be integrally formed by molded mode, and apical grafting part 231 and restricted part 232 are formed by same mould, and therefore, the height dimension of apical grafting part 231 and restricted part 232 has directly reflected the dimensional accuracy of mould.Because the dimensional accuracy of mould generally is controlled under tens of microns, so each face of apical grafting part 231 and restricted part 232 need not just to process especially and can obtain very high dimensional accuracy, thereby can realize very high manufacturing efficiency and very stable quality of product simultaneously.
In addition, the face shield in the present embodiment 233 is that the fluoride resin of representative is made in order to tetrafluoroethylene.
Tetrafluoroethylene is not had viscosity, and has high solid lubrication.Therefore, though since face shield 233 and exhaust reed 226 rub, the phenomenon of also almost blocking between its surface, very along sliding, so the abrasion that the Metal Contact of generation when exhaust reed 226 pushes up on the backstopping assembly 227 causes can be carried out inhibition.
In addition because tetrafluoroethylene has the character that does not take place to adhere, so exhaust reed 226 be easy to separate with backstopping assembly 227, thereby can prevent the delay phenomenon of closing of exhaust reed 226, the refrigerating capacity of raising closed compressor.
In addition, because tetrafluoroethylene has elasticity, attenuation vibration very capable, so the impact energy when apical grafting takes place for exhaust reed 226 and backstopping assembly 227 accesses mitigation, the generation of strike note also can be inhibited, exhaust reed 226 also can be prevented because of damaged phenomenon takes place in impact, thereby a kind of closed compressor very quiet, that reliability is high that works together can be provided.
During assembling, also be only to need will be in advance to be embedded on the backstopping assembly 227 and to get final product with fluoridizing based resin molded face shield 233, the manufacturing efficiency during assembling be also high.
In addition,, be to use to have ejusdem generis resin material such as polybutylene how (PBN), polybutylene terephthalate, sulfuration polyhenylene etc., also can get same effect and effect though what use in the present embodiment is tetrafluoroethylene.
In sum, closed compressor of the present invention can improve closes delay, improves the efficiency of energy utilization of closed compressor, therefore can use in air-conditioning, refrigeration equipment etc.
Claims (5)
1. closed compressor is characterized in that comprising:
The cylinder that piston moves back and forth therein;
The opening end of described cylinder is sealed, be provided with the valve plate of discharge valve apparatus simultaneously in a side opposite with cylinder; With
Be provided with the cylinder head of the exhaust chamber of packing into for described discharge valve apparatus,
Wherein, described discharge valve apparatus comprises: be located on the described valve plate, with described cylinder in the exhaust port that is connected; Be formed on the valve seat in the outside of described exhaust port; Make by the leaf spring material, have and make the switching part that described exhaust port opens and closes and the exhaust reed of bracketed part; With the backstopping assembly of the aperture that is used to limit described exhaust reed,
Described backstopping assembly and the corresponding position of described bracketed part on be provided with and described bracketed part between have the apical grafting part of predetermined gap.
2. the closed compressor described in claim 1 is characterized in that: described backstopping assembly also has and is in and opens and closes on the corresponding position of part, have a restricted part in the gap bigger than apical grafting part.
3. the closed compressor described in claim 1 or 2, it is characterized in that: described exhaust reed and backstopping assembly are fixed on the valve plate.
4. the closed compressor described in claim 1 or 2, it is characterized in that: described backstopping assembly is formed in the cylinder head.
5. the closed compressor described in claim 1 or 2 is characterized in that: the apical grafting face of described apical grafting part and restricted part is formed by solid lubricant.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005279710 | 2005-09-27 | ||
| JP2005279710A JP2007092539A (en) | 2005-09-27 | 2005-09-27 | Hermetic compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1940292A true CN1940292A (en) | 2007-04-04 |
Family
ID=37308896
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2006101388113A Pending CN1940292A (en) | 2005-09-27 | 2006-09-19 | Hermetic compressor |
| CNU2006201355098U Expired - Fee Related CN200985871Y (en) | 2005-09-27 | 2006-09-19 | Sealed-type compressor |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2006201355098U Expired - Fee Related CN200985871Y (en) | 2005-09-27 | 2006-09-19 | Sealed-type compressor |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20090010788A1 (en) |
| EP (1) | EP1809902A1 (en) |
| JP (1) | JP2007092539A (en) |
| KR (1) | KR100807002B1 (en) |
| CN (2) | CN1940292A (en) |
| WO (1) | WO2007037239A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102362070A (en) * | 2009-03-24 | 2012-02-22 | 松下电器产业株式会社 | Reciprocating compressor |
| CN107725329A (en) * | 2017-11-08 | 2018-02-23 | 福建雪人股份有限公司 | A kind of oil gas control device of Semi-closed piston compressor |
| CN116480820A (en) * | 2023-05-31 | 2023-07-25 | 安徽杰博恒创航空科技有限公司 | Compressor exhaust valve and rotor piston compressor |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4752257B2 (en) * | 2004-12-08 | 2011-08-17 | パナソニック株式会社 | Hermetic compressor |
| US20090291007A1 (en) * | 2006-04-27 | 2009-11-26 | Matsushita Electric Industrial Co., Ltd. | Hermetic compressor |
| JP2009036069A (en) * | 2007-08-01 | 2009-02-19 | Sanden Corp | Scroll type fluid machine |
| BRPI1105384B1 (en) * | 2011-12-20 | 2021-08-24 | Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda | ALTERNATIVE COMPRESSOR CYLINDER COVER |
| JP6130771B2 (en) * | 2013-11-08 | 2017-05-17 | 株式会社デンソー | Compressor and refrigeration cycle equipment |
| AT15377U1 (en) | 2016-07-06 | 2017-07-15 | Secop Gmbh | CYLINDER HEAD COVER FOR A REFRIGERANT COMPRESSOR |
| DE102018214369A1 (en) * | 2018-08-24 | 2020-02-27 | Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg | Valve assembly for an electrical refrigerant compressor |
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| KR100422363B1 (en) * | 2001-06-29 | 2004-03-12 | 삼성광주전자 주식회사 | Valve assembly for compressor |
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| EP1490598B1 (en) * | 2002-03-29 | 2006-11-29 | DeVilbiss Air Power Company | Head pressure relief assembly |
| KR100421965B1 (en) * | 2002-04-10 | 2004-03-11 | 삼성광주전자 주식회사 | Cylinder assembly of hermetic compressor |
| JP4752257B2 (en) * | 2004-12-08 | 2011-08-17 | パナソニック株式会社 | Hermetic compressor |
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- 2005-09-27 JP JP2005279710A patent/JP2007092539A/en active Pending
-
2006
- 2006-09-19 CN CNA2006101388113A patent/CN1940292A/en active Pending
- 2006-09-19 CN CNU2006201355098U patent/CN200985871Y/en not_active Expired - Fee Related
- 2006-09-20 US US11/659,136 patent/US20090010788A1/en not_active Abandoned
- 2006-09-20 WO PCT/JP2006/319094 patent/WO2007037239A1/en active Application Filing
- 2006-09-20 KR KR1020077004223A patent/KR100807002B1/en not_active IP Right Cessation
- 2006-09-20 EP EP06798352A patent/EP1809902A1/en not_active Withdrawn
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102362070A (en) * | 2009-03-24 | 2012-02-22 | 松下电器产业株式会社 | Reciprocating compressor |
| CN102362070B (en) * | 2009-03-24 | 2014-10-22 | 松下电器产业株式会社 | Reciprocating compressor |
| US9021937B2 (en) | 2009-03-24 | 2015-05-05 | Panasonic Intellectual Property Management Co., Ltd. | Reciprocating compressor |
| CN107725329A (en) * | 2017-11-08 | 2018-02-23 | 福建雪人股份有限公司 | A kind of oil gas control device of Semi-closed piston compressor |
| CN107725329B (en) * | 2017-11-08 | 2023-12-15 | 福建雪人股份有限公司 | Oil gas control device of semi-closed piston compressor |
| CN116480820A (en) * | 2023-05-31 | 2023-07-25 | 安徽杰博恒创航空科技有限公司 | Compressor exhaust valve and rotor piston compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20070061798A (en) | 2007-06-14 |
| CN200985871Y (en) | 2007-12-05 |
| JP2007092539A (en) | 2007-04-12 |
| US20090010788A1 (en) | 2009-01-08 |
| EP1809902A1 (en) | 2007-07-25 |
| WO2007037239A1 (en) | 2007-04-05 |
| KR100807002B1 (en) | 2008-02-25 |
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