CN108240332A - Closed rotating compressor and refrigerating air-conditioning - Google Patents
Closed rotating compressor and refrigerating air-conditioning Download PDFInfo
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- CN108240332A CN108240332A CN201711192662.3A CN201711192662A CN108240332A CN 108240332 A CN108240332 A CN 108240332A CN 201711192662 A CN201711192662 A CN 201711192662A CN 108240332 A CN108240332 A CN 108240332A
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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
- 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
- F04C18/32—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
- F04C18/322—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
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- 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
- F04C29/0021—Systems for the equilibration of forces acting on the pump
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The present invention provides a kind of closed rotating compressor, and the pressure for making the upper and lower end face of roller is balanced, makes the gap equalization of end face, and reduce the supply amount of working space of the lubricating oil into cylinder, improves performance and reliability.The closed rotating compressor has multiple rotary compression elements, rotary shaft, base bearing, supplementary bearing and spacing board, rotary compression element includes the cylinder with cylinder chamber and is accommodated in the roller of cylinder chamber, rotary shaft has eccentric part, roller is embedded in eccentric part, discharging valve device is respectively equipped in base bearing and supplementary bearing, at least any place in the end face of the base bearing of the end face sliding contact with roller and the end face both sides of supplementary bearing and the both ends of the surface with the spacing board of the end face sliding contact of roller is equipped with balancing slit.
Description
Technical field
The present invention relates to closed rotating compressor and refrigerating air-conditionings.
Background technology
In recent years, closed rotating compressor has two groups of rotary compression elements i.e. with the expansion of application range of capacity
The rotary compressor of the twin-tub type of cylinder is gradually standardized.Moreover, in this compressor, rated condition (100% load)
Performance and all critically important as the performance of the intermediate conditions (50% load) of sub-load, it is contemplated that the performance of intermediate conditions
APF (annual energy consumption efficiency：Annual Performance Factor) as energy-efficient evaluation index.
Moreover, in recent years, in order to become the Energy efficiency evaluation benchmark more to tally with the actual situation, have and be intended to be altered to be added to
The trend of the APF of performance during 25% load.Therefore, high efficiency during underload becomes important subject.
On the other hand, in recent years, from the viewpoint of being prevented global warming, as the refrigerant of refrigerating and air conditioning system, take
For existing R410A refrigerants, the small R32 refrigerants of coefficient that warm gradually are paid close attention to.
Patent document 1 discloses a kind of rotary compressor, and it is in ring respectively to consist of in a manner of the periphery for opening axle portion
It is recessed in low order side bearing to shape and low order side bearing load adjustment section is set, in the recess setting high-order side axle carrying of high-order side bearing
Lotus adjustment section thereby, it is possible to reduce the difference of the load for the top and bottom for acting on rolling piston (roller), can be reduced because of rolling piston
Squeeze slippage loss caused by low load side.
Existing technical literature
Patent document
Patent document 1：No. 4953974 bulletin of patent
Invention content
Problems to be solved by the invention
In rotary compressor disclosed in patent document 1, in low order side bearing load adjustment section and high-order side bearing load
Adjustment section annular in shape be recessed in a manner of the periphery for opening axle portion is set to inner circumferential.Therefore, in the low order for bearing thrust load
The upper surface recess setting low order side bearing load adjustment section of side bearing, has the part for eliminating load bearing plane, by axis
The lower end of the low order lateral deviation core in portion, which is pivotally supported, to be acted on the thrust load of axle portion and (dead weight of axle portion and rotor and acts on rotor
Magnetic thrust etc.) in the case of, it is difficult to bear the thrust load of axle portion.It in this case, for example, must be in lower face of axle portion etc.
The thrust bearing for being pivotally supported thrust load is reset, there are the subjects such as cost raising.In patent document 1, for acting on
The thrust load of the axle portion does not have any refer to.
In addition, in patent document 1, the pressure of the upper and lower end face of rolling piston is not because of caused by the inserting hole of intermediate plate
Equilibrium can be eliminated by low order side bearing load adjustment section and high-order side bearing load adjustment section.But about as rolling
The outlet of the discharging valve device of the unbalanced Another reason of pressure of the upper and lower end face of piston, does not carry out any carry
And as the unbalanced principal element of pressure, not as subject.
In closed rotating compressor, in general, leaf valve shape is arranged in the end plate in the bearing for the open end for blocking cylinder
The discharging valve device of formula, the working gas having compressed are discharged by the outlet of discharging valve device.Outlet flows to reduce
Go out resistance and the position for making a part prominent into cylinder is set on the shape engaged with being formed in the discharge notch of cylinder.Therefore, exist
Axis spin angular position at the end of discharge stroke, the outlet are installed on the end face of rolling piston.On the other hand, with phase
The intermediate plate side that the end face tossed about abuts becomes the unbalanced main cause of pressure there is no outlet.In rolling piston
Inner circumferential side there are the lubricating oil of high pressure, the lubricating oil is by the gap of upper and lower end face because pressure differential is and to the cylinder working of low pressure sky
Between internal leakage.Therefore, which is arranged for maintaining to the required least oil of the sealing function in cylinder working space
It measures critically important in terms of the raising of performance of compressor is realized.
Lubricating oil more than aequum causes the reduced performance of the compressor caused by loss on heating, churn loss etc..Separately
Outside, oil leak amount is proportional to the cube of end clearance.Therefore, it in order to reduce oil leak amount, needs to make rolling
The upper and lower end clearance equalization of piston.
But in rotary compressor disclosed in patent document 1, do not consider that pressure is unbalanced caused by outlet.Cause
This, there are following subjects：The pressure that the upper and lower end face of rolling piston is not implemented is balanced, and because in upper and lower end clearance generation
The influence of deviation, oil leak amount increase, and compressor performance reduces.
It is an object of the present invention in closed rotating compressor, the pressure for making the upper and lower end face of roller is balanced, makes end face
Gap equalization, and reduce the supply amount of working space of the lubricating oil into cylinder, improve performance and reliability.
Solution for solving the problem
To achieve these goals, closed rotating compressor of the invention have multiple rotary compression elements, rotary shaft,
Base bearing, supplementary bearing and spacing board, rotary compression element include the cylinder with cylinder chamber and are accommodated in the roller of cylinder chamber, rotary shaft
With eccentric part, roller is embedded in eccentric part, and discharging valve device is respectively equipped in base bearing and supplementary bearing, is slided with the end face of roller
The end face of the base bearing of contact and the end face both sides of supplementary bearing and in the both ends of the surface of the spacing board of the end face sliding contact of roller
At least any place be equipped with balancing slit.
The effect of invention
According to the present invention, in closed rotating compressor, the pressure that can make the upper and lower end face of roller is balanced, makes end face
Gap equalization, and the supply amount of working space of the lubricating oil into cylinder is reduced, therefore, it is possible to improve enclosed rotary compression
The performance and reliability of machine.In addition, by using this closed rotating compressor, the whole year of refrigerating air-conditioning can be improved
Energy consumption efficiency.
Description of the drawings
Fig. 1 is the longitudinal section view for the closed rotating compressor for representing one embodiment of the present invention.
Fig. 2 is A-A sectional elevations of Fig. 1.
Fig. 3 is B-O-B sectional views of Fig. 2.
Fig. 4 is comparable to the major part enlarged cross-sectional view of C-O-B sectional views of Fig. 2.
Fig. 5 is the exploded view of the position relationship for the balancing slit for representing Fig. 4.
Fig. 6 is the bottom view for the balancing slit for representing base bearing.
Fig. 7 is the vertical view for the balancing slit for representing supplementary bearing.
Fig. 8 is the vertical view for the balancing slit for representing spacing board.
Fig. 9 A are D-D sectional views of Fig. 8.
Fig. 9 B are the partial sectional views for the variation for representing Fig. 9 A.
Figure 10 is the partial, longitudinal cross-sectional for the closed rotating compressor for representing other embodiments of the present invention.
Figure 11 is the major part enlarged cross-sectional view for the closed rotating compressor for representing Figure 10.
Figure 12 is the exploded view of the position relationship for the balancing slit for representing Figure 11.
Figure 13 is the partial enlarged view of Figure 11.
Figure 14 is the vertical view for the supplementary bearing for representing Figure 13.
Figure 15 is E-E sectional views of Figure 14.
Figure 16 is the signal for representing to have the freeze cycle of the refrigerating air-conditioning of the closed rotating compressor of the present invention
Structure chart.
In figure：1-closed container, 2-rotary compression element, the rotary compression elements of 2A-first, the rotation pressures of 2B-second
Contracting unit, 3-motor part, 3a-stator, 3b-rotor, 4-rotary shaft, 4a, 4b-eccentric part, 4c, 4d-thrust portion,
5-spacing board, the-first cylinder of 5a-through hole, 6A, the cylinders of 6B-second, 7-base bearing, 7a, 8a-discharge cover, 7b, 8b-row
Go out valve gear, 7c, 8c-outlet, 7d, 8d-endless groove, 7e-base bearing inner face, 8-supplementary bearing, 8e-supplementary bearing inner face,
9a, 9b-roller, the cylinder chambers of 10a-first, 10b-second cylinder chamber, 11a, 11b-blade, 12a, 12b-leaf spring, 14-inhale
Enter pipe, 15-inlet box, 16a, 16b-suction line, 17a, 17b-suction passage, 18-discharge pipe, 19-lubricating oil, 20,
21st, 22,23-balancing slit, 21a-thrust face oil supply tank, 24-fixing bolt, 24a-bolt hole, 25-drain passageway, 30-
Closed rotating compressor, 31-freeze cycle, 32-condenser, 33-expansion valve, 34-evaporator, 35-refrigerant are matched
Pipe, 57,58-notch section, 67,68-valve pocket.
Specific embodiment
The closed rotating compressor of the present invention is such as applied to air conditioner, refrigerator.In addition, in the present specification,
Refrigerating air-conditioning is the general name of air conditioner, the refrigerator that freeze cycle is formed using closed rotating compressor etc..
Hereinafter, using attached drawing, the embodiment of the present invention will be described in detail.It is identical in the figure of each embodiment
Symbolic indication phase jljl or homologue.
Using Fig. 1~Fig. 9 B, the closed rotating compressor of the first embodiment of the present invention is illustrated.
Fig. 1 is the longitudinal section view for the closed rotating compressor for representing one embodiment of the present invention.Fig. 2 be Fig. 1 A-
A sectional elevations.Fig. 3 is B-O-B sectional views of Fig. 2.Fig. 4 is comparable to the major part amplification of C-O-B sectional views of Fig. 2
Sectional view.Fig. 5 is the exploded view of the Fig. 4 for the position relationship for illustrating each balancing slit shown in one embodiment of the present invention.Fig. 6 is
It is denoted as the plan view of the base bearing of the construction of the balancing slit of the feature of the present invention.Fig. 7 is the feature for being denoted as the present invention
Balancing slit construction supplementary bearing plan view.Fig. 8 is the interval of the construction for the balancing slit for being denoted as the feature of the present invention
The plan view of plate.Fig. 9 A are D-D sectional views of Fig. 8.Fig. 9 B represent the variation of Fig. 9 A.
In Fig. 1~Fig. 3,1 is closed container, in the multiple rotary compression elements 2 of the lower container of the closed container 1,
The motor part 3 of top storage driving rotary compression element, motor part 3 and rotary compression element 2 are linked by rotary shaft 4.
Motor part 3 includes the stator 3a for being fixed on the inner face of closed container 1 and the rotor 3b for being fixed on rotary shaft 4.Rotor 3b is arranged
To keep predetermined gap with the inside of stator 3a.In addition, motor part 3 is with controlling the converter (not shown) of operating frequency to be electrically connected
It connects.
Rotary compression element 2 includes the rotation pressures of the first rotary compression element 2A and second being arranged about 5 across spacing board
Contracting unit 2B.First rotary compression element 2A of upper side has the first cylinder 6A.On the other hand, the second rotary compression of lower side
Unit 2B has the second cylinder 6B.
The lower surface of the base bearing 7 of inner faces of the first cylinder 6A with being fixed on closed container 1 overlaps.In the following table of the second cylinder 6B
Face is equipped with supplementary bearing 8.Rotary shaft 4 rotates freely ground axle suspension by base bearing 7 and supplementary bearing 8.In rotary shaft 4, in the first cylinder
With the phase difference configuration of about 180 ゜, there are two eccentric part 4a, 4b for the position of the inside of 6A and the second cylinder 6B.In each eccentric part 4a, 4b
Periphery rotatably freely be fitted into have roller 9a, 9b (rolling piston).
First cylinder 6A and the second cylinder 6B mark off upper and lower surface by spacing board 5, base bearing 7 and supplementary bearing 8.In the first cylinder
The first cylinder chamber 10a is formed in 6A, second cylinder chamber 10b is formed in the second cylinder 6B.
The discharge cover 7a in the discharge space to form the working fluid having compressed is installed in base bearing 7.Discharge cover 7a coverings
It is assemblied in the discharging valve device 7b of the end plate of base bearing 7.Discharge cover 8a is also installed in supplementary bearing 8.Discharge cover 8a covering dresses
The discharging valve device 8b of end plate assigned in supplementary bearing 8.
The discharging valve device 7b of base bearing 7 is connected with the first cylinder chamber 10a, using compression, is risen in cylinder chamber 10a
It is opened during scheduled pressure, the working fluid having compressed is expelled in discharge cover 7a.The discharging valve device 8b of supplementary bearing 8 and
Two cylinder chambers 10b is connected, and using compression, is opened when rising to scheduled pressure in cylinder chamber 10b, the workflow that will be had compressed
Body is expelled in discharge cover 8a.
As shown in figure 3, it is accommodated with the reciprocal blade 11a being arranged freely in the cylinder chamber 10a of the first cylinder 6A.In the second cylinder 6B
Cylinder chamber 10b be similarly accommodated with blade 11b.Moreover, be accommodated with respectively in the rear end of blade 11a, 11b leaf spring 12a,
12b.Blade 11a, 11b are utilized respectively the peripheral part that the elastic force of leaf spring 12a, 12b make front end squeeze each roller 9a, 9b, right
Each roller 9a, 9b force.
The lower end of rotary shaft 4 is prominent to 8 lower section of supplementary bearing, is impregnated in the lubricating oil being detained in the bottom of closed container 1
In 19.Oil feed pump is installed in the lower face of rotary shaft 4, from here via fuel feeding access to form the second rotary compression element 2B
Lubricating oil is supplied with each sliding part of the component of the first rotary compression element 2A.
In Fig. 1,14 be to flow into the inlet box 15 with gas-liquid separating function from external refrigerating circuit for working fluid
Suction line.It is connected in the bottom of inlet box 15 as the suction line 16a of the first sucking piping and as the second sucking piping
Suction line 16b.Suction line 16a, 16b and compressor connect.Suction line 16a is via the suction passage 17a for being formed in the first cylinder 6A
And with being connected in the first cylinder chamber 10a.Suction line 16b is via being formed in the suction passage 17b and second cylinder chamber 10b of the second cylinder 6B
Connection.
Symbol 18 is the discharge pipe that the working fluid of the high pressure in closed container 1 is made to flow out to external refrigerating circuit.Separately
Outside, symbol 25 is to guide the working fluid being expelled in the discharge cover 8a of downside to the discharge in the discharge cover 7a of upside to lead to
Road.In addition, in Fig. 2, symbol 24 is the fixing bolt of assemble compressible unit.
Using Fig. 4~Fig. 9 B, the construction of the pressure equilibrium of the realization roller upper and lower end face of the present invention is illustrated.
Fig. 4 is comparable to the major part enlarged cross-sectional view of C-O-B sectional views of Fig. 2.Fig. 5 is in order to illustrate the present invention
An embodiment shown in each balancing slit position relationship and eliminate rotary shaft 4, the first cylinder 6A, the second cylinder 6B, roller from Fig. 4
The exploded view of 9a, 9b and discharging valve device 7b, 8b.
In present embodiment, the localized contact of the locality of rotary shaft 4 and bearing in order to prevent, in the cylinder 6A of base bearing 7
The end face of side is formed with endless groove 7d.Similarly, it is formed with endless groove 8d in the end face of the cylinder 6B sides of supplementary bearing 8.In addition, revolving
The end face of the bearing side of the eccentric part 4a of shaft 4 is formed with thrust portion 4c.Moreover, the bearing side of the eccentric part 4b in rotary shaft 4
End face be formed with thrust portion 4d.Thereby, it is possible to support shaft thrust load.
In addition, the discharging valve device 7b of Fig. 4 is set to the bottom of the valve pocket 67 of Fig. 5.In addition, the discharging valve device 8b of Fig. 4
It is set to the bottom of the valve pocket 68 of Fig. 5.
Through hole 5a is formed in spacing board 5.Rotary shaft 4 is inserted into base bearing 7, through hole 5a and supplementary bearing 8.
Symbol 20 is formed at the balancing slit (base bearing balancing slit) of the periphery of the endless groove 7d of base bearing 7.The balancing slit
20 outer diameter be and the outside diameter d for the through hole 5a for being formed in spacing board 5mRoughly the same size.In other words, balancing slit 20 is outer
The internal diameter d of diameter and through hole 5amIt is roughly equal.The outer diameter of balancing slit 20 and the outside diameter d of through hole 5amDifference be preferably, with perforation
The internal diameter d of hole 5amFor denominator, within ± 0.3%.Internal diameter Di1Than the internal diameter d of base bearing 7s1Greatly, and as in endless groove 7d
Inner circumferential side ensure thrust portion 4c bearing plane construction.
Symbol 21 is formed at the balancing slit (supplementary bearing balancing slit) of the periphery of the endless groove 8d of supplementary bearing 8.The balancing slit
21 outer diameter also be and the outside diameter d for the through hole 5a for being formed in spacing board 5mRoughly the same size.In other words, balancing slit 21
The internal diameter d of outer diameter and through hole 5amIt is roughly equal.The outer diameter of balancing slit 21 and the outside diameter d of through hole 5amDifference be preferably, to pass through
The diameter d of through-hole 5amFor denominator, within ± 0.3%.Internal diameter Di2Than the internal diameter d of supplementary bearing 8s2Greatly.The situation of present embodiment
Under, make ensures the construction of the bearing plane of thrust portion 4d in the inner circumferential side of endless groove 8d and peripheral side.
Utilize balancing slit 20,21, it can be ensured that the bearing plane of the shaft thrust load acted on due tos dead weight of rotary shaft 4 etc.,
And the pressure that can eliminate the roller upper and lower end face because of caused by the through hole 5a for being formed in spacing board 5 is unbalanced.In addition, pass through
Balancing slit 20,21 is set, and the pressure that can eliminate roller upper and lower end face is unbalanced, can reduce leakage of the lubricating oil to cylinder chamber etc.
Amount further, it is possible to ensure to separate the thickness of valve pocket 67,68 and the wall between endless groove 7d, 8d, is able to maintain that base bearing 7 and pair
The intensity of bearing 8.
In addition, the unbalanced effect of pressure that can be eliminated either one of balancing slit 20,21, it is preferred that tool
There are balancing slit 20,21 both sides.
Symbol 22,23 is formed at the balancing slit (spacing board balancing slit) of spacing board 5.
The balancing slit 22 for being formed in the upper surface of spacing board 5 is to be in and the row for the discharging valve device 7b for being disposed in base bearing 7
Export identical shape (the diameter d of 7c (outlet mouth)p1), and in the depth across same projection position recess setting opposed cylinder 6A
Spend the shallow slot of below 0.1mm.In other words, it is configured to, is projected by balancing slit 22 and outlet 7c to orthogonal with rotary axis direction
Face when, balancing slit 22 and outlet 7c outer edge overlapping.In this case, the deviation of the overlapping of two outer edges is preferably opposite
It is within 0.8% in the diameter of outlet 7c.
The balancing slit 23 for being formed in the lower face of spacing board 5 is to be in and the row for the discharging valve device 8b for being set to supplementary bearing 8
Export identical shape (the diameter d of 8c (outlet mouth)p2) and in the depth across same projection position recess setting opposed cylinder 6B
Spend the shallow slot of below 0.1mm.In other words, it is configured to, is projected by balancing slit 23 and outlet 8c to orthogonal with rotary axis direction
Face when, balancing slit 23 is Chong Die with the outer edge of outlet 8c.In this case, the deviation of the overlapping of two outer edges is preferably opposite
It is within 0.8% in the diameter of outlet 8c.
In short, balancing slit 22,23 is formed in the both ends of the surface of spacing board 5.
Using these balancing slits 22,23, the pressure that can eliminate the roller upper and lower end face because of caused by outlet 7c, 8c is uneven
Weighing apparatus.In addition, pressure can be obtained either one of only balancing slit 22,23 eliminates unbalanced effect, it is preferred that having
Balancing slit 22,23 both sides.
According to the above, it can realize that the pressure of roller upper and lower end face is balanced, therefore roller upper and lower end face gap can be made equal
Deng change, the supply of working space of the lubricating oil into cylinder is remained into minimum limit.
Here, how to be eliminated to balancing slit 20,21,22,23, pressure is unbalanced further to be illustrated.
It is assumed that in the case of no balancing slit 20,21,22,23, the internal side diameter of roller 9a, 9b be in closed container
The identical pressure in portion, still, due to spacing board 5 through hole 5a and be disposed in outlet 7d, 8d of base bearing 7, supplementary bearing 8,
The range for acting on the pressure of roller upper and lower end face is different, therefore the load for acting on roller upper and lower surface is different, and roller is extruded into low
Load side.In contrast, in the case of with balancing slit 20,21,22,23, can make to act on the pressure of roller upper and lower end face
It is essentially equal, therefore the load for acting on roller upper and lower surface is equal.
Balancing slit 20,21,22,23 each serves as effect, if all of which is set, effect is best.
In addition, it is equipped with notch section 57 in cylinder 6A.Thereby, it is possible to reduce the fluid out of cylinder chamber 10a by outlet 7c
Flow path resistance.In addition, it is equipped with notch section 58 in cylinder 6B.Thus, it is possible to reduce 10b passes through outlet 8c out of cylinder chamber fluid
Flow path resistance.
Next, the action of the closed rotating compressor to forming in this way illustrates.
In Fig. 1, when the stator 3a to motor part 3 is powered, rotor 3b is driven, by 8 axis of base bearing 7 and supplementary bearing
The rotary shaft 4 of bearing is driven in rotation.Then, rotatably freely it is embedded in the roller of the periphery of each eccentric part 4a, 4b of rotary shaft 4
9a, 9b are eccentrically rotated in each cylinder 6A, 6B, carry out the compression operation of working fluid.
The working fluid of low pressure, by inlet box 15, and passes through each suction line 16a, 16b and is imported into each cylinder from suction line 14
Cylinder chamber 10a, 10b of 6A, 6B and compressed.The working fluid for the high pressure having compressed is by being assemblied in base bearing 7 or supplementary bearing 8
Discharge valve portion 7b, 8b of end plate is flowed out in discharge cover 7a, 8a, and outside is expelled to from closed container 1 by discharge pipe 18
Refrigerating circuit.The lubrication of each sliding part of closed rotating compressor is configured to, and with the driving of rotary shaft 4, generation is installed on
The centrifugation pumping action of the oil feed pump of the lower face of rotary shaft 4 extracts and lodges in the lubricating oil 19 of 1 bottom of closed container, and via
The fuel feeding access (not shown) being formed in rotary shaft 4 supplies lubricating oil to the sliding part of each rotary compression element 2A, 2B.
Next, using Fig. 6~Fig. 9 B, the construction of each balancing slit of the feature as the present invention is illustrated.
Fig. 6 is the bottom view of base bearing.
In detail in this figure, from the central part of setting rotary shaft, there is base bearing inner face 7e, endless groove is formed on the outside of it
7d.It is formed with balancing slit 20 outward from the peripheral part of endless groove 7d.The internal diameter of balancing slit 20 is equal with the outer diameter of endless groove 7d.
In other words, endless groove 7d and balancing slit 20 form the connected slot with step.The inner peripheral portion of balancing slit 20 can also be formed as
The shape being open to endless groove 7d.Endless groove 7d and balancing slit 20 are recessed slot.
In addition, in figure 6, symbol 24a is the bolt hole of fixing bolt 24 shown in Fig. 2.
Fig. 7 is the vertical view of supplementary bearing.
In this figure, from the central part of setting rotary shaft, there is supplementary bearing inner face 8e, endless groove is formed on the outside of it
8d.Balancing slit 21 is formed on the outside of endless groove 8d.The internal diameter of balancing slit 21 is bigger than the outer diameter of endless groove 8d.Therefore, it presses
Slot 21 and endless groove 8d are without the part that is overlapped.In other words, balancing slit 21 is to be formed in ring-type across shaft thrust load bearing plane
The recessed slot of the peripheral side of slot 8d.
Fig. 8 is the vertical view of spacing board.
In this figure, through hole 5a is formed in the central portion of spacing board 5.
In assembled state, balancing slit 22 is formed in the position opposed with the outlet 7c of base bearing 7 shown in Fig. 4
It puts.In this regard, according to will be seen below：Spacing board 5 shown in this figure is inverted, when Chong Die with base bearing 7 shown in fig. 6, is pressed
Slot 22 is Chong Die with the outlet 7c of base bearing 7.
Fig. 9 A and 9B are D-D sectional views of Fig. 8, show the section shape for the balancing slit 22 for being formed in spacing board 5.
In Fig. 9 A, balancing slit 22 is made in shape (the diameter d identical with being formed in the outlet 7c of base bearing 7p1) and it is deep
Degree δ is the shallow slot of below 0.1mm (fixed value).That is, in the case of this figure, balancing slit 22 is that recess is set as simple cylinder
The slot of the spot-facing of shape.
It, can be by the increasing of dead volume caused by the formation because of balancing slit 22 by the way that balancing slit 22 is made such shape
Add and be suppressed to minimum limit, the pressure for eliminating the roller upper and lower end face because of caused by outlet is unbalanced.
In addition, the regulation that the depth δ of balancing slit 22 is set as to below 0.1mm can according to the discharge capacity of compressor, operating condition
How much to change.The prescribed depth δ in a manner of becoming less than the 5% of volume of outlet mouth by the volume for making balancing slit 22,
It disclosure satisfy that the requirement specification of present embodiment.If more than 5%, refrigerant gas is easily detained, the gas of delay it is swollen again
The harmful effect of swollen performance becomes larger, therefore the possibility that cannot get desired performance enhancing effects increases.Here, outlet
The volume in portion refers to the volume in outlet 7c shown in Fig. 4 (hole of cylindrical shape).
In figures 9 b and 9, by the way that balancing slit 22 is shaped to roughly conical shape, so as to make the increase of dead volume into one
Step is reduced.The depth in most deep is δ, and δ is set as below 0.1mm.In addition, for being formed in the end face position opposed with balancing slit 22
The balancing slit 23 of (lap position at the back side of spacing board 5) is put, because similary with balancing slit 22, is omitted the description.
Using Figure 10~Figure 15, the closed rotating compressor of second embodiment of the present invention is illustrated.
Figure 10 is the longitudinal section view of the closed rotating compressor shown in present embodiment.Figure 11 is the major part of Figure 10
Enlarged cross-sectional view.Figure 12 is the exploded view of the Figure 11 for the position relationship for illustrating each balancing slit shown in present embodiment.Figure 13 is
The partial enlarged view of Figure 11.Figure 14 is the plan view of the supplementary bearing of the Figure 13 for the shape for representing balancing slit.Figure 15 be Figure 14 E-
E sectional views.In figure, the component for being labelled with the symbol identical with Fig. 1 is identical component, plays identical effect.
In present embodiment, the endless groove 7d of first embodiment is not formed in the end face of the cylinder 6A sides of base bearing 7.Equally
Ground does not form the endless groove 8d of first embodiment in the end face of the cylinder 6B sides of supplementary bearing 8 yet.
In this case, the outer diameter for being formed in the balancing slit 20 of the end face of the cylinder 6A sides of base bearing 7 is also with being formed in interval
The outside diameter d of the through hole 5a of plate 5mRoughly the same size, internal diameter Di1Than the internal diameter d of base bearing 7s1Greatly.Moreover, than balancing slit
20 ensure the bearing plane of the thrust portion 4c of rotary shaft 4 by 4 side of rotary shaft.
The outer diameter for being formed in the balancing slit 21 of the end face of the cylinder 6B sides of supplementary bearing 8 is the through hole with being formed in spacing board 5
The outside diameter d of 5amRoughly the same size, internal diameter Di2Than the internal diameter d of supplementary bearing 8s2Greatly.Moreover, leaning on rotary shaft 4 than balancing slit 21
Side ensures the bearing plane of the thrust portion 4d of rotary shaft 4.
The balancing slit 22 for being formed in the upper surface of spacing board 5 is in being disposed in base bearing in the same manner as first embodiment
Shape (diameter d identical the outlet 7c of 7 discharging valve device 7bp1), and across identical projected position opposed cylinder 6A
The shallow slot of below the depth 0.1mm of recess setting.In addition, be formed in the lower face of spacing board 5 balancing slit 23 be in arranging
In identical shape (the diameter d of the outlet 8c of the discharging valve device 8b of supplementary bearing 8p2), and across opposed identical of cylinder 6B
The shallow slot of below the depth 0.1mm of projected position recess setting.
In addition, as shown in Figure 13~15, present embodiment is configured to, in the inner circumferential for the balancing slit 21 for being formed in supplementary bearing 8
The thrust bearing plane 8f settings connection supplementary bearing inner face 8e of the side and thrust face oil supply tank 21a of balancing slit 21, via the oil supply tank
Fuel feeding is carried out, thus keeps the lubrication between thrust bearing plane 8f and the thrust portion 4d of rotary shaft 4 well.
Using above-described balancing slit 20,21,22,23, it can realize that the pressure of roller upper and lower end face is balanced.Therefore, energy
Enough make the gap equalization of roller upper and lower end face, the supply of the lubricating oil of the working space out of each roller inner circumferential cylinder is remained most
Small limit limit.Moreover, thereby, it is possible to improve the performance of closed rotating compressor and reliability.
In addition, to having, there are two the closed rotating compressors of rotary compression element to be said in above-mentioned record
It is bright, but the closed rotating compressor of the present invention is without being limited thereto, can also apply to the rotation for being overlapped three or more
The closed rotating compressor of the structure of compression unit.
Next, using the structure chart of the freeze cycle shown in Figure 16, to being equipped with the closed rotating compressor of the present invention
The concrete example of refrigerating air-conditioning illustrate.
Figure 16 is the freeze cycle (refrigerating air-conditioning) for the closed rotating compressor for having embodiments of the present invention
Schematic diagram.Freeze cycles of the R32 as working fluid (refrigerant) is used here, illustrating.R32 is greenhouse effects of the earth system
Number (GWP) is smaller more all the time than the refrigerant R410A used in refrigerating and air conditioning system and from the viewpoint for preventing greenhouse effects of the earth
Set out the refrigerant being concerned in recent years.
In Figure 16, the component for being labelled with the symbol identical with Fig. 1 is identical component, plays identical effect.Freezing follows
Ring 31 has closed rotating compressor 30.Symbol 32 is condenser, and symbol 33 is expansion valve, and symbol 34 is evaporator, by it
Be sequentially connected by refrigerant piping 35, so as to constitute freeze cycle 31.
Next, illustrate the flowing of refrigerant.
The refrigerant for the high temperature and pressure discharged from closed rotating compressor 30 enters condenser 32 and radiates, temperature drop
It is low.The refrigerant come out from the condenser 32 enters expansion valve 33, becomes the gas-liquid two-phase refrigerant of low-temp low-pressure, and discharge.
The gas-liquid two-phase refrigerant come out from expansion valve 33 enters evaporator 34 and absorbs heat, and so as to gasify, returns to enclosed rotary compression
Machine 30 is compressed, is similarly recycled repeatedly again.As a result, if refrigerating plant, then cooled object is cooled down with evaporator 34.If
For air-conditioning device, then formed and cool down the refrigeration operation of room air or with 32 heating indoor air of condenser with evaporator 34
Heating operation.
In addition, the situation that working fluid is R32 is illustrated in the explanation of Figure 16, but the present invention is not limited to
This, can also apply to use the situation of other working fluids.
More than, in accordance with the invention it is possible to provide the gap equalization for making each roller end face and performance and envelope of excellent in reliability
Enclosed rotary compressor can realize the raising of the performance and reliability of refrigerating and air conditioning system.
Claims (10)
1. a kind of closed rotating compressor, which is characterized in that have：
Multiple rotary compression elements；
Rotary shaft；
Base bearing；
Supplementary bearing；And
Spacing board,
Above-mentioned rotary compression element includes the cylinder with cylinder chamber and is accommodated in the roller of above-mentioned cylinder chamber,
Above-mentioned rotary shaft has eccentric part,
Above-mentioned roller is embedded in above-mentioned eccentric part,
Discharging valve device is respectively equipped in above-mentioned base bearing and above-mentioned supplementary bearing,
At least one party in the end face of the above-mentioned base bearing of the end face sliding contact with above-mentioned roller and the end face of above-mentioned supplementary bearing
Equipped with balancing slit.
2. closed rotating compressor according to claim 1, which is characterized in that
The internal diameter of through hole of the outer diameter of above-mentioned balancing slit with being formed in above-mentioned spacing board is roughly equal.
3. closed rotating compressor according to claim 2, which is characterized in that
The difference of the outer diameter of above-mentioned balancing slit and the diameter of above-mentioned through hole, with above-mentioned a diameter of denominator of above-mentioned through hole, is in
Within ± 0.3%.
4. closed rotating compressor described in any one of claim 1 to 3, which is characterized in that
The internal diameter of above-mentioned balancing slit is bigger than the outer diameter of above-mentioned rotary shaft.
5. a kind of closed rotating compressor, which is characterized in that have：
Multiple rotary compression elements；
Rotary shaft；
Base bearing；
Supplementary bearing；And
Spacing board,
Above-mentioned rotary compression element includes the cylinder with cylinder chamber and is accommodated in the roller of above-mentioned cylinder chamber,
Above-mentioned rotary shaft has eccentric part,
Above-mentioned roller is embedded in above-mentioned eccentric part,
Discharging valve device is respectively equipped in above-mentioned base bearing and above-mentioned supplementary bearing,
At least one party in the both ends of the surface of the above-mentioned spacing board of the end face sliding contact with above-mentioned roller is equipped with balancing slit.
6. closed rotating compressor according to claim 5, which is characterized in that
It is above-mentioned when projecting the outlet mouth of above-mentioned balancing slit and above-mentioned discharging valve device to the face orthogonal with rotary axis direction
The outer edge of balancing slit and above-mentioned outlet mouth is overlapped.
7. closed rotating compressor according to claim 6, which is characterized in that
The volume of above-mentioned balancing slit be above-mentioned outlet mouth volume less than 5%.
8. a kind of closed rotating compressor, which is characterized in that have：
Multiple rotary compression elements；
Rotary shaft；
Base bearing；
Supplementary bearing；And
Spacing board,
Above-mentioned rotary compression element includes the cylinder with cylinder chamber and is accommodated in the roller of above-mentioned cylinder chamber,
Above-mentioned rotary shaft has eccentric part,
Above-mentioned roller is embedded in above-mentioned eccentric part,
Discharging valve device is respectively equipped in above-mentioned base bearing and above-mentioned supplementary bearing,
The end face of the above-mentioned base bearing of the end face sliding contact with above-mentioned roller and above-mentioned supplementary bearing end face both sides and with it is upper
The both ends of the surface for stating the above-mentioned spacing board of the end face sliding contact of roller are equipped with balancing slit.
9. according to closed rotating compressor according to any one of claims 1 to 8, which is characterized in that with as workflow
Body is connected R32 as the freeze cycle of refrigerant.
10. a kind of refrigerating air-conditioning, which is characterized in that
Have：Closed rotating compressor according to any one of claims 1 to 9, condenser, expansion valve and evaporator,
And they are connected by refrigerant piping.
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| Application Number | Priority Date | Filing Date | Title |
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| JP2016-252858 | 2016-12-27 | ||
| JP2016252858A JP6568841B2 (en) | 2016-12-27 | 2016-12-27 | Hermetic rotary compressor and refrigeration air conditioner |
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| CN108240332B CN108240332B (en) | 2020-02-14 |
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| CN114555948A (en) * | 2019-10-24 | 2022-05-27 | 日立江森自控空调有限公司 | Compressor and refrigeration cycle device |
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| CN113167276B (en) * | 2018-12-12 | 2023-04-14 | 东芝开利株式会社 | Rotary compressor and refrigeration cycle device |
| JP7170547B2 (en) * | 2019-01-21 | 2022-11-14 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle equipment |
| JP7470567B2 (en) * | 2019-10-24 | 2024-04-18 | 日立ジョンソンコントロールズ空調株式会社 | Compressor and refrigeration cycle device |
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| JP2011117309A (en) * | 2009-11-30 | 2011-06-16 | Toshiba Carrier Corp | Rotary compressor and refrigerating cycle device |
| CN103511253A (en) * | 2012-11-14 | 2014-01-15 | 广东美芝制冷设备有限公司 | Rotary compressor and multiple-cylinder rotary compressor |
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| JPH04143483A (en) * | 1990-10-05 | 1992-05-18 | Daikin Ind Ltd | Compressor with rolling piston |
| KR20050011523A (en) * | 2003-07-23 | 2005-01-29 | 삼성전자주식회사 | Variable capacity rotary compressor |
| JP2015049006A (en) * | 2013-09-03 | 2015-03-16 | ダイキン工業株式会社 | Refrigeration device |
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| JP2011117309A (en) * | 2009-11-30 | 2011-06-16 | Toshiba Carrier Corp | Rotary compressor and refrigerating cycle device |
| CN103511253A (en) * | 2012-11-14 | 2014-01-15 | 广东美芝制冷设备有限公司 | Rotary compressor and multiple-cylinder rotary compressor |
| CN104838145A (en) * | 2013-03-26 | 2015-08-12 | 东芝开利株式会社 | Multiple-cylinder rotary compressor and refrigeration cycle device |
| CN205036575U (en) * | 2015-09-17 | 2016-02-17 | 广东美芝制冷设备有限公司 | Multi -cylinder rotary compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN114555948A (en) * | 2019-10-24 | 2022-05-27 | 日立江森自控空调有限公司 | Compressor and refrigeration cycle device |
| CN114555948B (en) * | 2019-10-24 | 2023-01-10 | 日立江森自控空调有限公司 | Compressor and refrigeration cycle device |
Also Published As
| Publication number | Publication date |
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| CN108240332B (en) | 2020-02-14 |
| JP6568841B2 (en) | 2019-08-28 |
| JP2018105243A (en) | 2018-07-05 |
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