CN110418892A - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
- Publication number
- CN110418892A CN110418892A CN201880017804.9A CN201880017804A CN110418892A CN 110418892 A CN110418892 A CN 110418892A CN 201880017804 A CN201880017804 A CN 201880017804A CN 110418892 A CN110418892 A CN 110418892A
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- China
- Prior art keywords
- cylinder body
- discharge chambe
- suction passage
- axial direction
- height
- 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
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
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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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
-
- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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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
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/102—Adjustment of the interstices between moving and fixed parts of the machine by means other than fluid pressure
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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
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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
- F04C2240/00—Components
- F04C2240/10—Stators
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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
- F04C2240/00—Components
- F04C2240/20—Rotors
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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
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/806—Pipes for fluids; Fittings therefor
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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
- F04C2250/00—Geometry
- F04C2250/10—Geometry of the inlet or outlet
- F04C2250/101—Geometry of the inlet or outlet of the inlet
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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
- F04C2250/00—Geometry
- F04C2250/20—Geometry of the rotor
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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
- F04C2250/00—Geometry
- F04C2250/30—Geometry of the stator
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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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/17—Tolerance; Play; Gap
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Control Of Motors That Do Not Use Commutators (AREA)
- Supercharger (AREA)
Abstract
A kind of rotary compressor comprising the first cylinder body and the second cylinder body arranged in the axial direction of drive shaft, wherein be formed with suction passage, the suction passage will be provided from the refrigerant that external equipment is provided via suction line to each discharge chambe.Surface area of the surface area in the region faced in the second cylinder body with suction passage less than the region faced in the first cylinder body with suction passage.Second cylinder body in the height in the axial direction and the difference in the height in the axial direction of piston that is configured in the discharge chambe of the second cylinder body less than the first cylinder body in the height in the axial direction and the difference (A3-A4 < A1-A2) of the height in the axial direction of piston that is configured in the discharge chambe of the first cylinder body.Therefore, the inhibition that the miniaturization and compressor efficiency that can take into account compressor reduce.
Description
Technical field
The present invention relates to the rotary compressors for being for example used for air conditioner etc..
Background technique
Japanese Unexamined Patent Publication 2016-118142 bulletin is disclosed with upper cylinder body and lower cylinder body and in the discharge chambe of each self-forming
In the rotary compressor of twin-rotor housing that refrigerant is compressed.Gas-liquid separator is installed in the side of compressor.In gas
There are two suction lines for liquid/gas separator connection.A suction line in two suction lines is connected to upper cylinder body, another suction line
It is connected to lower cylinder body.Refrigerant is provided from gas-liquid separator to upper cylinder body and lower cylinder body via each suction line.In upper cylinder body and
Piston is configured in the discharge chambe that lower cylinder body is respectively formed, the piston has roller.Discharge chambe is divided into be imported by piston
The low-pressure chamber of refrigerant and the hyperbaric chamber that refrigerant is compressed.
Existing technical literature
Patent document
Patent document 1: Japanese Unexamined Patent Publication 2016-118142 bulletin
Summary of the invention
Subject to be solved by the invention
In the case where minimizing the rotary compressor of twin-rotor housing, it is preferred that gas-liquid separator etc. is for providing
The external equipment of refrigerant also minimizes.But if two suction lines are connected to gas-liquid separator, it is difficult to realize gas-liquid point
Miniaturization from device.As its countermeasure, it is contemplated that by utilizing a suction line by the rotary compressor and gas-liquid of twin-rotor housing
Separator connects, so that gas-liquid separator be made to minimize.But in this case, since the branch of suction line makes to suck
Resistance increases, and compressor efficiency may reduce.
The object of the present invention is to provide the rotary compressions that can minimize and be able to suppress compressor efficiency reduction
Machine.
Means for solving the problems
Rotary compressor of the invention accommodates compression mechanism and driving mechanism, and the driving mechanism has to the pressure
The drive shaft that contracting mechanism is driven, wherein the compression mechanism has: multiple cylinder bodies, they are respectively formed with discharge chambe, and
And by the drive shaft be located at multiple compressions it is indoor in a manner of arrange in the axial direction of the drive shaft；Multiple end plates
Part, they are configured in the both ends in the axial direction of each cylinder body, and divide the discharge chambe；With multiple pistons, their quilts
Configuration is driven in the inside of each discharge chambe by the drive shaft.The multiple cylinder body includes the first cylinder body and the second cylinder body, described
Second cylinder body is adjacent with first cylinder body across an end plate member, is formed with sucking in the rotary compressor
Access, the suction passage include: the first access, by the refrigerant provided from external equipment via suction line to described first
The discharge chambe of cylinder body provides；And alternate path, it is from the access of first forehearth limb, and to second cylinder
The discharge chambe of body provides refrigerant.The surface area in the region faced in second cylinder body with the suction passage is less than institute
State the surface area in the region faced in the first cylinder body with the suction passage.Also, second cylinder body in the axial direction
Height and the piston being configured in the discharge chambe of second cylinder body the height in the axial direction difference
Less than the institute in the height in the axial direction and the discharge chambe for being configured in first cylinder body of first cylinder body
State the difference of the height in the axial direction of piston.
External equipment either gas-liquid separator, be also possible to be configured in gas-liquid separator with it is of the invention rotary
Arbitrary equipment between compressor.
In the present invention, it is also possible to first access by first cylinder body and does not pass through second cylinder body,
The alternate path, from first forehearth limb, passes through first cylinder body and described second in the inside of first cylinder body
Cylinder body both sides.
In the present invention, it is also possible to the suction line to be configured to, it is intracorporal first cylinder can be located at its end
Mode is inserted into first cylinder body.
In the present invention, it is also possible to the suction line to be configured to, first cylinder can be located relative to its end
Body and configure and be inserted into the end plate member with the mode in the end plate member of the second cylinder body opposite side.
In addition, in the present invention, it is preferred that being faced in the cylinder body with the suction passage in the multiple cylinder body
Region surface area it is smaller, the cylinder body in the axial direction height be configured in the cylinder body the discharge chambe in
The difference of the height in the axial direction of the piston is smaller.
Also, in the present invention, it is preferred that about any of the multiple cylinder body, if the cylinder body described
Height in axial direction is Hc (mm), set the piston for being configured in the inside for the discharge chambe for being formed in the cylinder body in institute
The height in axial direction is stated to be Hp (mm), set the surface area in the region faced with the suction passage in the cylinder body as As (mm2)、
If the length on the direction orthogonal with the axial direction of the suction passage in the cylinder body is Ls (mm), meet:
3.9 × 0.0001≤(Hc-Hp)/Hc-1.4 × 0.0001 × As/ (HcLs)≤6.7 × 0.0001
Invention effect
It is formed with suction passage in rotary compressor of the invention, the suction passage includes: the first access, will system
Cryogen is provided to the discharge chambe of the first cylinder body；And alternate path, it is from the access of the first forehearth limb, and to the second cylinder body
Discharge chambe provide refrigerant.In addition, the surface area in the region faced in the second cylinder body with suction passage is less than in the first cylinder body
The surface area in the region faced with suction passage.Therefore, compared with the first cylinder body, in the cylinder body of the second cylinder body and suction passage
Temperature caused by the refrigerant of the areas adjacent faced reduces few.Therefore, in the second cylinder body and the pressure for being configured in the second cylinder body
It contracts between indoor piston, temperature difference becomes smaller, and the difference of size changing amount when thermal expansion becomes smaller.Therefore, in the rotary compression
In machine, about the second cylinder body, compared with the first cylinder body, by by the difference of the height of cylinder body and the height of piston (that is, the axis of piston
The gap between end face in the axial direction of upward end face and end plate member) it reduces, to make from piston inner peripheral portion to discharge chambe
Oil leak reduce, improve volumetric efficiency and diagram efficiency as a result,.Therefore, though using suction line by two cylinder bodies
In the case where being connected to make compressor to minimize with external equipment, since volumetric efficiency and diagram efficiency can be passed through
It improves and is therefore able to suppress the drop of compressor efficiency to compensate the reduction of the compressor efficiency as caused by the increase of suction resistance
It is low.That is, the inhibition of miniaturization and the compressor efficiency reduction of compressor can be taken into account.
Detailed description of the invention
Fig. 1 is the figure for showing the rotary compressor of first embodiment of the invention together with gas-liquid separator.
Fig. 2A is the top view of the upper cylinder body of rotary compressor shown in FIG. 1.
Fig. 2 B is the top view of the lower cylinder body of rotary compressor shown in FIG. 1.
Fig. 3 is the partial enlarged view of the compression mechanism of rotary compressor shown in FIG. 1.
Fig. 4 is the figure for showing the rotary compressor of second embodiment of the present invention.
Fig. 5 A is the top view of the upper cylinder body of rotary compressor shown in Fig. 4.
Fig. 5 B is the top view of the lower cylinder body of rotary compressor shown in Fig. 4.
Fig. 6 is the partial enlarged view of the compression mechanism of rotary compressor shown in Fig. 4.
Fig. 7 is the figure for showing the rotary compressor of third embodiment of the present invention.
Fig. 8 is the partial enlarged view of the compression mechanism of rotary compressor shown in Fig. 7.
Fig. 9 is the chart for showing the experimental result carried out about multiple rotary compressors.
Specific embodiment
[first embodiment]
Firstly, being illustrated referring to figs. 1 to rotary compressor 1 of the Fig. 3 to first embodiment.As shown in Figure 1, this reality
The compressor 1 for applying mode is the rotary compressor of bi-cylinder, with closed container 2 and is accommodated in closed container 2
Driving mechanism 3 and compression mechanism 4.Closed container 2 is the cylindric container that upper and lower ends are blocked.In closed container 2
Side is equipped with gas-liquid separator 5.Gas-liquid separator 5 is connected to pressure by means of a suction line 6 for importing refrigerant
Contracting mechanism 4.The top of closed container 2 is provided with discharge pipe 7, the discharge pipe 7 is used for will be compressed in compression mechanism 4
Refrigerant discharge.Lubricating oil is contained in the bottom of closed container 2.
Compressor 1 such as in air conditioner in the refrigeration that use, will be provided from suction line 6 is provided in refrigerating cycle
Agent compression is simultaneously discharged from discharge pipe 7.In compressor 1, such as R32 or R410A have been used as refrigerant.1 quilt of compressor
It is arranged to direction shown in FIG. 1, the i.e. axial direction of compressor 1 court for up and down direction (identical as the axial direction of aftermentioned drive shaft 3b)
To.
Setting driving mechanism 3 is for driving compression mechanism 4, and driving mechanism 3 is by becoming the motor 3a of driving source and being mounted
It is constituted in the drive shaft 3b of motor 3a.Motor 3a includes: substantially circular stator 3aa, is fixed in the interior of closed container 2
Circumferential surface；Substantially circular rotor 3ab, the radially inner side of stator 3aa is configured in across air gap.Rotor 3ab has magnetic
Body (illustration omitted), stator 3aa have coil (illustration omitted).
Drive shaft 3b is fixed in the inner peripheral surface of rotor 3ab, with rotor 3ab integrally from then to the progress of compression mechanism 4
Driving.Drive shaft 3b is respectively provided with eccentric part 3c, 3d (referring to Fig. 2A, Fig. 2 B in aftermentioned discharge chambe 31 and in discharge chambe 51
And Fig. 3).Eccentric part 3c, 3d be all formed as it is cylindric, central shaft relative to the rotation center of drive shaft 3b and it is eccentric.Inclined
Center portion 3c, 3d is separately installed with the piston 32,52 of compression mechanism 4.
In addition, being formed with oil passage (illustration omitted) in the inside of the downside of drive shaft 3b substantially half.Oil passage is along upper
Lower direction extends and in many places to the radial branching of drive shaft 3b.The pump of helical blade shape is installed in the lower end of drive shaft 3b
Lubricating oil is drawn into oil passage by component (illustration omitted), the pump part with the rotation of drive shaft 3b.By pump part
From the lower end of drive shaft 3b be drawn come lubricating oil from the side of drive shaft 3b be discharged and be provided to such as discharge chambe 31,
Each sliding part of the compression mechanisms 4 such as 51.
Compression mechanism 4 includes upper silencer 10a, 10b, upper cover 20 (end plate member), upper cylinder body 30 (cylinder body), intermediate plate 40
(end plate member), lower cylinder body 50 (cylinder body), lower cover 60 (end plate member) and lower silencer 70.They along drive shaft 3b axial direction
It sequentially arranges from the top down.
As shown in figure 1 and 2 a, upper cylinder body 30 is the component of roughly circular plate.It is formed in the central portion of upper cylinder body 30
Discharge chambe 31, the discharge chambe 31 are the round holes that upper cylinder body 30 is penetrated through in the axial direction of drive shaft 3b.Match in discharge chambe 31
It is equipped with piston 32.Piston 32 is constituted by circular roller 32a and from the periphery of roller 32a towards the blade 32b that radial outside extends.
Roller 32a is configured in discharge chambe 31 in a manner of it can be installed in the outer peripheral surface of eccentric part 3c with the relative rotation.
As illustrated in figs. 2 a and 3, the radially extending horizontal passageway 30a conduct in upper cylinder body 30 is formed in upper cylinder body 30
Suction passage for importing from refrigerant to discharge chambe 31.The radially inner side end of horizontal passageway 30a is open in discharge chambe 31, horizontal
The radial outside end of access 30a is open in the outer peripheral surface of upper cylinder body 30.Suction line 6 is from the radial outside end of horizontal passageway 30a
It is inserted into horizontal passageway 30a, end is located near the center of horizontal passageway 30a.In addition, being formed in upper cylinder body 30 from horizontal logical
The vertical access 30b that road 30a extends to vertical lower section is as the suction passage for importing refrigerant to discharge chambe 51.Vertical access
30b branch between the radially inner side end of horizontal passageway 30a and the terminal position of suction line 6, and to extend below vertical and
The lower surface of upper cylinder body 30 is open.
In addition, as shown in Figure 2 A, the shape being recessed from the peripheral wall of discharge chambe 31 towards radial outside is formed in upper cylinder body 30
The blade containment portion 33 of shape.Configured with the opposed pairs bushing 34 in the circumferential direction of upper cylinder body 30 in blade containment portion 33.One
It is shape made of half-and-half dividing generally cylindrical component to bushing 34.A pair of of bushing 34 is configured with blade between them
It can be swung in blade containment portion 33 in the state of 32b.In addition, blade 32b is configured between a pair of of bushing 34
In the radially advance and retreat of upper cylinder body 30.Discharge chambe 31 is divided into low-pressure chamber and hyperbaric chamber by means of blade 32b.
As shown in Figure 1, upper cover 20 is configured to the upper end face contact with upper cylinder body 30, by by the upper end seal of discharge chambe 31
It closes, to divide discharge chambe 31.Upper cover 20 is that substantially circular component is extended rotatably through inserted with drive in the central portion
Moving axis 3b.Upper cover 20 is fixed in the inner peripheral surface of closed container 2 by welding etc..
Upper silencer 10a, 10b are configured in the top of upper cover 20.Between upper cover 20 and upper silencer 10b and upper noise elimination
Muffler space is formed between device 10a and upper silencer 10b.The discharge of adjoint refrigerant can be realized using upper muffler space
The reduction of noise.
As shown in Figure 2 A, upper cover 20 is provided with tap 35, the tap 35 makes discharge chambe 31 and upper muffler space
It is connected to and the compressed upward muffler space of refrigerant will be discharged in discharge chambe 31.Tap 35 (is saved by the dump valve of plate
Sketch map shows) blocking.When the pressure of discharge chambe 31 become defined pressure more than when, dump valve flexible deformation and beat tap 35
It opens.
Intermediate plate 40 is the component of circular plate, as shown in Figure 1, being configured to and the lower end surface of upper cylinder body 30 and lower cylinder body
50 upper end face contact.It is compressed as shown in figure 3, intermediate plate 40 is divided and blocking the lower end of the discharge chambe 31 of upper cylinder body 30
Room 31, and discharge chambe 51 is divided and the upper end closed by the discharge chambe 51 of lower cylinder body 50.Intermediate plate 40 be formed with
The vertical access 40a of the vertical access 30b connection of upper cylinder body 30 is as the suction passage for importing refrigerant to discharge chambe 51.It is vertical
Access 40a connects the horizontal passageway 50a of the vertical access 30b and aftermentioned lower cylinder body 50 of upper cylinder body 30.
As shown in fig. 1 and fig. 2b, across intermediate plate 40 and the lower cylinder body 50 adjacent with upper cylinder body 30 and upper cylinder body 30 are same
Ground is the component of roughly circular plate.It is formed with discharge chambe 51 in the central portion of lower cylinder body 50, the discharge chambe 51 is to drive
The round hole of lower cylinder body 50 is penetrated through in the axial direction of axis 3b.Piston 52 is configured in discharge chambe 51.Piston 52 is by circular roller
52a and the blade 52b composition extended from the periphery of roller 52a towards radial outside.Roller 52a can be installed on partially with the relative rotation
The mode of the outer peripheral surface of center portion 3d is configured in discharge chambe 51.
As shown in Fig. 2 B and Fig. 3, the radially extending horizontal passageway 50a conduct in lower cylinder body 50 is formed in lower cylinder body 50
Suction passage for importing from refrigerant to discharge chambe 51.Horizontal passageway 50a shape and the upper surface notch by lower cylinder body 50
At.The radially inner side end of horizontal passageway 50a is open in discharge chambe 51.The radial outside end of horizontal passageway 50a is radially by under
The wall surface of cylinder body 50 is blocked and is open upwards.As shown in figure 3, the radial outside end of horizontal passageway 50a is via opening above this
Mouthful and connect with the vertical access 40a of intermediate plate 40.The part of the removing opening in horizontal passageway 50a is by the following table of intermediate plate 40
Face blocking.
In addition, as shown in Figure 2 B, the shape being recessed from the peripheral wall of discharge chambe 51 towards radial outside is formed in lower cylinder body 50
The blade containment portion 53 of shape.Configured with the opposed pairs bushing 54 in the circumferential direction of lower cylinder body 50 in blade containment portion 53.One
It is shape made of half-and-half dividing generally cylindrical component to bushing 54.A pair of of bushing 54 is configured with blade between them
It can be swung in blade containment portion 53 in the state of 52b.In addition, blade 52b is configured between a pair of of bushing 54
In the radially advance and retreat of lower cylinder body 50.Discharge chambe 51 is divided into low-pressure chamber and hyperbaric chamber by means of blade 52b.
As shown in Figure 1, lower cover 60 is configured to the lower end face contact with lower cylinder body 50, by by the lower end seal of discharge chambe 51
It closes, to divide discharge chambe 51.Lower cover 60 is that substantially circular component is extended rotatably through inserted with drive in the central portion
Moving axis 3b.
Lower silencer 70 is configured in the lower section of lower cover 60.It is empty that lower noise elimination is formed between lower cover 60 and lower silencer 70
Between.The reduction of the noise of the discharge with refrigerant can be realized using lower muffler space.
As shown in Figure 2 B, lower cover 60 is provided with tap 55, the tap 55 makes discharge chambe 51 and lower muffler space
It is connected to and the compressed downward muffler space of refrigerant will be discharged in discharge chambe 31.Tap 55 (is saved by the dump valve of plate
Sketch map shows) blocking.When the pressure of discharge chambe 51 become defined pressure more than when, dump valve flexible deformation and beat tap 55
It opens.
Lower muffler space is via being respectively formed in passing through for lower cover 60, lower cylinder body 50, intermediate plate 40, upper cylinder body 30 and upper cover 20
Through-hole and be connected to upper muffler space.
It is formed with suction passage in the rotary compressor 1 of present embodiment, the suction passage includes: upper suction passage
(the first access) provides refrigerant to the discharge chambe 31 of upper cylinder body 30；It is from upper with lower suction passage (alternate path)
The access of suction passage (the first access) branch, and refrigerant is provided to the discharge chambe 51 of lower cylinder body 50.In this embodiment party
In formula, upper suction passage is formed at the end slave suction line 6 in the horizontal passageway 30a of upper cylinder body 30 to the level of discharge chambe 31
Access, by upper cylinder body 30 and pass through lower cylinder body 50.Lower suction passage by be formed in upper cylinder body 30 vertical access 30b,
It is formed in the vertical access 40a of intermediate plate 40 and is formed in the horizontal passageway 50a composition of lower cylinder body 50 (referring to Fig. 3).Lower suction passage
Pass through 50 both sides of upper cylinder body 30 and lower cylinder body.
In other words, the horizontal access of the end slave suction line 6 in horizontal passageway 30a to discharge chambe 31 (does not include horizontal logical
The end slave suction line 6 to the radial outside end of horizontal passageway 30a in the 30a of road) and vertical access 30b formed in upper cylinder body 30
Suction passage.Also, horizontal passageway 50a forms suction passage in lower cylinder body 50.In the present embodiment, in lower cylinder body 50
The surface area in the region faced with suction passage is less than the surface area in the region faced in upper cylinder body 30 with suction passage.
" surface area in the region faced in cylinder body with suction passage " is the inner peripheral surface that the wall of suction passage is formed in cylinder body
Surface area, and be the surface area of wall surface in cylinder body for passing through from the refrigerant that gas-liquid separator 5 sucks.Therefore, upper cylinder half
The surface area in the region faced in body 30 with suction passage is and the end slave suction line 6 in horizontal passageway 30a to discharge chambe 31
The summation of the surface area and the surface area with indulging the region that access 30b is faced in region that faces of horizontal access, lower cylinder body 50
In the surface area in region that is faced with suction passage be surface area with the region faced horizontal passageway 50a.
In the lesser lower cylinder body 50 of surface area in the region faced compared with upper cylinder body 30 with suction passage, with upper cylinder body
30 compare, and temperature caused by the refrigerant of the areas adjacent faced with suction passage reduces few.Therefore, lower cylinder body 50 with matched
It is placed between the piston 52 of the discharge chambe 51 of lower cylinder body 50, temperature difference becomes smaller, and the difference of size changing amount when thermal expansion becomes smaller.
Therefore, in the compressor of present embodiment 1, as shown in figure 3, the height A3 of lower cylinder body 50 and being configured at lower cylinder body
The difference of the height A4 of the piston 52 of 50 discharge chambe 51 is less than the height A1 of upper cylinder body 30 and is configured at the discharge chambe of upper cylinder body 30
The difference (A3-A4 < A1-A2) of the height A2 of 31 piston 32.Here, the height A2 of the height A1 of upper cylinder body 30 and piston 32 it
The difference of the height A4 of the height A3 and piston 52 of difference and lower cylinder body 50 is value when compressor 1 stops (when room temperature).
It is formed with suction passage in the rotary compressor 1 of present embodiment, the suction passage includes: that upper sucking is logical
Road provides refrigerant to the discharge chambe 31 for the upper cylinder body 30 connecting with suction line 6；It is from upper suction with lower suction passage
Enter the access of forehearth limb, and provides refrigerant to the discharge chambe of lower cylinder body 50 51.Also, lower cylinder body 50 and suction passage
The surface area in the region faced is less than the surface area in the region of upper cylinder body 30 faced with suction passage.Therefore, with upper cylinder body 30
It compares, in lower cylinder body 50, temperature caused by the refrigerant of the areas adjacent faced with suction passage in cylinder body reduces few.Cause
This, between the piston 52 in lower cylinder body 50 and the discharge chambe 51 for being configured in lower cylinder body 50, temperature difference becomes smaller, when thermal expansion
The difference of size changing amount becomes smaller.Therefore, in lower cylinder body 50, compared with upper cylinder body 30, even if by the end in the axial direction of piston 52
The gap shrinks between end face in the axial direction of face and end plate member 40,60 adjacent thereto are also not susceptible to obstacle.In turn, by
This, by reducing the oil leak from piston inner peripheral portion to discharge chambe, so as to improve volumetric efficiency and diagram efficiency, therefore, i.e.,
Make using a suction line 6 be connected to two cylinder bodies 30,50 and the gas-liquid separator 5 to minimize compressor 1
In the case of, the drop of the compressor efficiency as caused by the increase of suction resistance is compensated by the raising of volumetric efficiency and diagram efficiency
It is low, it is able to suppress the reduction of compressor efficiency.In this way, in the present embodiment, the miniaturization and compression of compressor 1 can be taken into account
The inhibition that engine efficiency reduces.
In addition, in the present embodiment, upper suction passage (the first access) passes through upper cylinder body 30 and does not pass through lower cylinder body 50,
Lower suction passage (alternate path) passes through upper cylinder body 30 and lower cylinder body 50 from upper suction passage branch in the inside of upper cylinder body 30
Both sides.Thereby, it is possible to be readily derived such structure: the surface area in the region faced in lower cylinder body 50 with suction passage is less than
The surface area in the region faced in upper cylinder body 30 with suction passage.
Also, in the present embodiment, suction line 6, which is configured to be located at the mode in upper cylinder body 30 with its end, is inserted
Enter into upper cylinder body 30.The access of the refrigerant of the discharge chambe 31 from the end of suction line 6 to upper cylinder body 30 is constituted as a result, only
For linear horizontal passageway 30a, it is able to suppress the increase of suction resistance.
[second embodiment]
In the following, being illustrated referring to compressor of the fig. 4 to fig. 6 to second embodiment.In the compression of first embodiment
In machine 1, the case where being inserted into upper cylinder body 30 is configured to the suction line 6 of gas-liquid separator 5 and is illustrated, but this embodiment party
The compressor 101 of formula is configured to be inserted into 120 this respect of upper cover and first embodiment in the suction line 6 of gas-liquid separator 5
It is different.In addition, in the present embodiment, to having the identical label of the part mark of structure same as the first embodiment
And the description thereof is omitted as appropriate.
The compressor 101 of present embodiment accommodates driving mechanism 3 and compression mechanism 104.In the compressor 101, such as scheme
Shown in 5A and Fig. 6, as the suction passage for importing refrigerant into the discharge chambe 31 of upper cylinder body 130, relative to upper
Cylinder body 130 and be configured in and be formed with the upper cover 120 of 50 opposite side of lower cylinder body in the radially extending horizontal logical of upper cover 120
The road 120a and vertical access 120b extended from horizontal passageway 120a to vertical lower section.The radially inner side end of horizontal passageway 120a is in radial direction
On be capped 120 wall surface blocking, and be open downwards.The radially inner side end of horizontal passageway 120a via the opening below this and
It is connect with the horizontal passageway 130a of upper cylinder body 130.The radial outside end of horizontal passageway 120a is open in the outer peripheral surface of upper cover 120.It inhales
Enter pipe 6 to be inserted into horizontal passageway 120a from horizontal passageway 120a, end is located near the center of horizontal passageway 120a.
It is formed in upper cylinder body 130 and is used as in the radially extending horizontal passageway 130a of upper cylinder body 130 for by refrigerant
The suction passage imported to the discharge chambe 31 of upper cylinder body 130.Horizontal passageway 130a shape and the upper surface notch by upper cylinder body 130
At.The radially inner side end of horizontal passageway 130a is open in discharge chambe 31.The radial outside end of horizontal passageway 130a radially by
The wall surface of upper cylinder body 130 blocks, and is open upwards.The radial outside end of horizontal passageway 130a via the opening above this and with
The vertical access 120b connection of upper cover 120.The lower surface for being capped 120 in addition to the part of the opening of horizontal passageway 130a blocks.
It is used as in addition, being formed with vertical access 130b from horizontal passageway 130a to vertical that extend below from upper cylinder body 130 for by refrigerant
The suction passage imported to the discharge chambe 51 of lower cylinder body 150.Vertical access 130b prolongs from horizontal passageway 130a branch and to vertical lower section
It stretches and is open in the lower surface of upper cylinder body 130.
The vertical access 40a connecting with the vertical access 130b of upper cylinder body 130 is formed in intermediate plate 40 to be used as that will freeze
The suction passage that agent is imported to the discharge chambe 51 of lower cylinder body 50.Vertical access 40a by the vertical access 130b of upper cylinder body 130 with it is aftermentioned
The horizontal passageway 50a of lower cylinder body 50 is connected.
As shown in figs. 5 b and 6, it is formed with across the lower cylinder body 50 adjacent with upper cylinder body 130 of intermediate plate 40 in lower cylinder body
50 radially extending horizontal passageway 50a is as the suction passage for importing refrigerant to discharge chambe 51.Horizontal passageway 50a is logical
It crosses the upper surface notch by lower cylinder body 50 and is formed.The radially inner side end of horizontal passageway 50a is open in discharge chambe 51.Horizontal passageway
The radial outside end of 50a is blocked by the wall surface of lower cylinder body 50 radially, and is open upwards.As shown in fig. 6, horizontal passageway
The radial outside end of 50a is connect via the opening above this with the vertical access 40a of intermediate plate 40.Removing in horizontal passageway 50a
The part of the opening is blocked by the lower surface of intermediate plate 40.
It is formed with suction passage in the rotary compressor 101 of present embodiment, the suction passage includes: that upper sucking is logical
Road (the first access) provides refrigerant to the discharge chambe 31 of upper cylinder body 130；With lower suction passage (alternate path), it is
Refrigerant is provided from the access of upper suction passage (the first access) branch, and to the discharge chambe of lower cylinder body 50 51.In this implementation
In mode, upper suction passage is by the end slave suction line 6 that is formed in the horizontal passageway 120a of upper cover 120 to horizontal passageway 50a's
The horizontal access of radially inner side end and vertical access 120b and the horizontal passageway 130a for being formed in upper cylinder body 130 are constituted.Lower suction
Enter access by being formed in the vertical access 130b of upper cylinder body 130, being formed in the vertical access 40a of intermediate plate 40 and being formed in lower cylinder body 50
Horizontal passageway 50a constitute (referring to Fig. 6).
In other words, horizontal passageway 130a and vertical access 130b form suction passage in upper cylinder body 130.Also, horizontal passageway
50a forms suction passage in lower cylinder body 50.In the present embodiment, the region faced in lower cylinder body 50 with suction passage
Surface area is less than the surface area in the region faced in upper cylinder body 130 with suction passage.
In the lesser lower cylinder body 50 of surface area in the region faced compared with upper cylinder body 130 with suction passage, with upper cylinder half
Body 130 is compared, and temperature caused by the refrigerant of the areas adjacent faced with suction passage reduces few.Therefore, lower cylinder body 50 with
It is configured between the piston 52 of the discharge chambe 51 of lower cylinder body 50, temperature difference becomes smaller, and the difference of size changing amount when thermal expansion becomes
It is small.
Therefore, in the compressor of present embodiment 101, as shown in fig. 6, the height A3 of lower cylinder body 50 and being configured at lower cylinder
The difference of the height A4 of the piston 52 of the discharge chambe 51 of body 50 is less than the height A1 of upper cylinder body 130 and is configured at the pressure of upper cylinder body 130
The difference (A3-A4 < A1-A2) of the height A2 of the piston 32 of contracting room 31.Here, the height of the height A1 of upper cylinder body 130 and piston 32
When the difference of the height A4 of the height A3 and piston 52 of the difference and lower cylinder body 50 of degree A2 is the stopping of compressor 101 (when room temperature)
Value.
It is formed with suction passage in the rotary compressor 101 of present embodiment, the suction passage includes: that upper sucking is logical
Road provides refrigerant to the discharge chambe 31 of upper cylinder body 130；It is from the logical of upper suction passage branch with lower suction passage
Road, and refrigerant is provided to the discharge chambe of lower cylinder body 50 51.Also, the table in the region of lower cylinder body 50 faced with suction passage
Area is less than the surface area in the region of upper cylinder body 130 faced with suction passage.Therefore, compared with upper cylinder body 130, in lower cylinder body
In 50, temperature caused by the refrigerant of the areas adjacent faced with suction passage in cylinder body reduces few.Therefore, in lower cylinder body 50
Between the piston 52 in the discharge chambe 51 for being configured in lower cylinder body 50, temperature difference becomes smaller, size changing amount when thermal expansion it
Difference becomes smaller.Therefore, in lower cylinder body 50, compared with upper cylinder body 130, even if by end face in the axial direction of piston 52 and adjacent thereto
End plate member 40,60 axial direction on end face between gap shrinks be also not susceptible to obstacle.In turn, pass through reduction as a result,
From piston inner peripheral portion to the oil leak of discharge chambe, so as to improve volumetric efficiency and diagram efficiency, therefore, even if utilizing one
Two cylinder bodies 130,50 and gas-liquid separator 5 are connected in the case where minimizing compressor 101 by suction line 6, are led to
The raising of volumetric efficiency and diagram efficiency is crossed to compensate the reduction of the compressor efficiency as caused by the increase of suction resistance, can be pressed down
The reduction of compressor efficiency processed.In this way, in the present embodiment, miniaturization and the compressor efficiency of compressor 101 can be taken into account
Reduced inhibition.
In addition, in the present embodiment, upper suction passage (the first access) passes through upper cylinder body 130 and does not pass through lower cylinder body
50, lower suction passage (alternate path) passes through upper cylinder body 30 and lower cylinder from upper suction passage branch in the inside of upper cylinder body 130
50 both sides of body.Thereby, it is possible to be readily derived such structure: the surface area in the region faced in lower cylinder body 50 with suction passage
Less than the surface area in the region faced in upper cylinder body 130 with suction passage.
Also, in the present embodiment, suction line 6 is configured to be located relative to the configuration of upper cylinder body 130 with its end
Upper cover 120 is being inserted into the mode in end plate member, that is, upper cover 120 of 50 opposite side of lower cylinder body.Upper sucking is logical as a result,
The position that direction of travel of the road in upper cylinder body 130 with a refrigerant changes from vertical to level, lower suction passage is under
The position that direction of travel in cylinder body 50 with a refrigerant changes from vertical to level.That is, in upper suction passage and lower suction
Enter suction resistance in access and is not likely to produce biggish difference.
[third embodiment]
In the following, being illustrated referring to compressor of the Fig. 7 and Fig. 8 to third embodiment.In the compression of third embodiment
In machine 1, the suction line 6 of gas-liquid separator 5, which is configured to be inserted in 250 this respect of lower cylinder body, to be different from the first embodiment.
In addition, in the present embodiment, fitted to having the identical label of the part mark of structure same as the first embodiment
It is local that the description thereof will be omitted.
The compressor 201 of present embodiment accommodates driving mechanism 3 and compression mechanism 204.As shown in Figure 7 and Figure 8, as with
In the suction passage for importing refrigerant to the discharge chambe 51 of lower cylinder body 250, it is formed in lower cylinder body 250 in lower cylinder body 250
Radially extending horizontal passageway 250a.The radially inner side end of horizontal passageway 250a is open in discharge chambe 51, the diameter of horizontal passageway 250a
Outside side end is open in the outer peripheral surface of lower cylinder body 250.Suction line 6 is inserted into cross from the radial outside end of horizontal passageway 250a
In access 250a, end is located near the center of horizontal passageway 250a.In addition, being formed in lower cylinder body 250 from horizontal passageway 250a
The vertical access 250b extended above to vertical is as leading to refrigerant to the sucking that the discharge chambe 31 of upper cylinder body 230 imports
Road.Vertical access 250b branch and on vertical between the radially inner side end of horizontal passageway 250a and the terminal position of suction line 6
Fang Yanshen and the upper surface of lower cylinder body 250 be open.Also, it is formed with below from horizontal passageway 250a to vertical in lower cylinder body 250
The vertical access 250c extended.Vertical access 250c is between the radially inner side end of horizontal passageway 250a and the terminal position of suction line 6
(position Chong Die with vertical access 250b or more) branch is simultaneously open to extension below vertical in the lower surface of lower cylinder body 250.It should
Opening is closed by lower cover 60.
The vertical access 240a connecting with the vertical access 250b of lower cylinder body 250 is formed in intermediate plate 240 to be used as that will make
The suction passage that cryogen is imported to discharge chambe 31.Access 240a is indulged by the vertical access 250b of lower cylinder body 250 and aftermentioned upper cylinder body
230 horizontal passageway 230a is connected.
Across intermediate plate 240 and the upper cylinder body 230 adjacent with lower cylinder body 250 be formed with upper cylinder body 230 radially
The horizontal passageway 230a of extension is as the suction passage for importing refrigerant to discharge chambe 31.Horizontal passageway 230a is by by upper cylinder half
The lower surface notch of body 230 and formed.The radially inner side end of horizontal passageway 230a is open in discharge chambe 31.The diameter of horizontal passageway 230a
Outside side end is blocked by the wall surface of upper cylinder body 230 radially, and is open downwards.The radial outside end of horizontal passageway 230a
It is connect via the opening below this with the vertical access 240a of intermediate plate 240.In horizontal passageway 230a in addition to the opening portion
Divide and is blocked by the upper surface of intermediate plate 240.
It is formed with suction passage in the rotary compressor 201 of present embodiment, the suction passage includes: that lower sucking is logical
Road (the first access) provides refrigerant to the discharge chambe 51 of lower cylinder body 250；With upper suction passage (alternate path), it is
Refrigerant is provided from the access of lower suction passage (the first access) branch, and to the discharge chambe of upper cylinder body 230 31.In this implementation
In mode, lower suction passage is formed at the end slave suction line 6 in the horizontal passageway 250a of lower cylinder body 250 to discharge chambe 51
Horizontal access, upper suction passage is by being formed in the vertical access 250b of lower cylinder body 250, being formed in the vertical access of intermediate plate 240
240a and the horizontal passageway 230a for being formed in upper cylinder body 230 are constituted.
In other words, the horizontal access of the end slave suction line 6 in horizontal passageway 250a to discharge chambe 51 (does not include horizontal logical
The end slave suction line 6 to the radial outside end of horizontal passageway 250a in the 250a of road) and vertical access 250b in lower cylinder body 250
Form suction passage.Also, horizontal passageway 230a forms suction passage in upper cylinder body 230.In the present embodiment, upper cylinder half
The surface area in the region faced in body 230 with suction passage is less than the surface in the region faced in lower cylinder body 250 with suction passage
Product.
In the lesser upper cylinder body 230 of surface area in the region faced compared with lower cylinder body 250 with suction passage, with lower cylinder
Body 250 is compared, and temperature caused by the refrigerant of the areas adjacent faced with suction passage reduces few.Therefore, upper cylinder body 230 with
It is configured between the piston 32 of the discharge chambe 31 of upper cylinder body 230, temperature difference becomes smaller, and the difference of size changing amount when thermal expansion becomes
It is small.
Therefore, in the compressor of present embodiment 201, as shown in figure 8, the height A1 of upper cylinder body 230 and being configured at
The difference of the height A2 of the piston 32 of the discharge chambe 31 of cylinder body 230 is less than the height A3 of lower cylinder body 250 and is configured at lower cylinder body 250
The difference (A1-A2 < A3-A4) of the height A4 of the piston 52 of discharge chambe 51.Here, the height A3 of lower cylinder body 250 and piston 52
When the difference of the height A2 of the difference of height A4 and the height A1 of upper cylinder body 230 and piston 32 are the stopping of compressor 201 (when room temperature)
Value.
It is formed with suction passage in the rotary compressor 201 of present embodiment, the suction passage includes: that lower sucking is logical
Road provides refrigerant to the discharge chambe 51 of lower cylinder body 250；It is from the logical of lower suction passage branch with upper suction passage
Road, and refrigerant is provided to the discharge chambe of upper cylinder body 230 31.Also, the region of upper cylinder body 230 faced with suction passage
Surface area is less than the surface area in the region of lower cylinder body 250 faced with suction passage.Therefore, compared with lower cylinder body 250, in upper cylinder half
In body 230, temperature caused by the refrigerant of the areas adjacent faced with suction passage in cylinder body reduces few.Therefore, in upper cylinder half
Between body 230 and the piston 32 being configured in the discharge chambe 31 of upper cylinder body 230, temperature difference becomes smaller, and size when thermal expansion becomes
The difference of change amount becomes smaller.Therefore, in upper cylinder body 230, compared with lower cylinder body 250, even if by the axial direction of piston 32 end face and
The gap shrinks between end face in the axial direction of end plate member 20,240 adjacent thereto are also not susceptible to obstacle.In turn, as a result,
By reducing the oil leak from piston inner peripheral portion to discharge chambe, so as to improve volumetric efficiency and diagram efficiency, therefore, even if
It is connected to two cylinder bodies 230,250 and the gas-liquid separator 5 to minimize compressor 201 using a suction line 6
In the case of, the drop of the compressor efficiency as caused by the increase of suction resistance is compensated by the raising of volumetric efficiency and diagram efficiency
It is low, it is able to suppress the reduction of compressor efficiency.In this way, in the present embodiment, the miniaturization and pressure of compressor 201 can be taken into account
The inhibition that contracting engine efficiency reduces.
In addition, in the present embodiment, lower suction passage (the first access) passes through lower cylinder body 250 and does not pass through upper cylinder body
230, upper suction passage (alternate path) passes through lower cylinder body 250 and upper from lower suction passage branch in the inside of lower cylinder body 250
230 both sides of cylinder body.Thereby, it is possible to be readily derived such structure: the table in the region faced in upper cylinder body 230 with suction passage
Area is less than the surface area in the region faced in lower cylinder body 250 with suction passage.
Also, in the present embodiment, suction line 6 is configured to the mode quilt being located in lower cylinder body 250 with its end
It is inserted in lower cylinder body 250.The access of the refrigerant of the discharge chambe 51 from the end of suction line 6 to lower cylinder body 250 is constituted as a result,
Only linear horizontal passageway 250a, is able to suppress the increase of suction resistance.
[verification test of real machine]
Here, the test result carried out about multiple rotary compressors is illustrated.As described above, of the invention
In rotary compressor, compared with the first cylinder body, the second cylinder body is subtracted by reducing the difference of the height of cylinder body and the height of piston
Few oil leak from piston inner peripheral portion to discharge chambe, to improve compressor efficiency.The difference of the height of the height and piston of cylinder body
It is smaller more to can be improved compressor efficiency, on the other hand, it is easy to happen and is glued as caused by the sliding friction of piston and end plate member
, reliability reduces.In other words, the difference of the height of the height and piston of cylinder body is bigger, is more not susceptible to piston and end plate member
Sliding friction caused by adhesion and reliability improve, on the other hand, compressor efficiency reduce.
Accordingly, with respect to could ensure reliability and obtain admissible compressor efficiency, the present inventor uses multiple rotations
Formula compressor (including several types) has carried out confirmatory test.In this experiment, the height Hc in drive shaft axial direction of cylinder body
(mm), be configured in the height Hp (mm) in the axial direction of the piston for being formed in the inside of discharge chambe of cylinder body, cylinder body with suction
Enter the surface area As (mm in the region that access faces2), the length Ls (mm) of the suction passage of cylinder body be parameter.Length Ls is and drive
The length of the axial suction passage in orthogonal plane of moving axis, is the length in the radial direction of cylinder body in the above-described embodiment
Degree.The example of length Ls is shown as L1, L2 in Fig. 3, Fig. 6 and Fig. 8.
About each compressor for making aforementioned four parameter Hc, Hp, As, Ls variation, to whether piston and end plate member occurring
Sliding friction caused by adhesion and admissible compressor efficiency whether can be obtained evaluated.Fig. 9 is to depict it
As a result chart.
In Fig. 9, the parameter of the longitudinal axis is (difference (Hc-Hp)/height of cylinder Hc of the height of cylinder body and piston), indicates companion
The change rate of the height of cylinder varied with temperature.When cylinder body the areas adjacent faced with suction passage temperature due to refrigerant
When reduction, cylinder body is heat-shrinked, and therefore, and the difference (Hc-Hp) of height of piston becomes smaller.Also, if it is zero, piston is held
Plate component is sandwiched and is adhered, and compressor is possible to damage.The the numerical value of the longitudinal axis the big more is not susceptible to adhere.
The parameter of horizontal axis is that (the surface area As/ height of cylinder Hp × sucking in the region faced in cylinder body with suction passage is logical
Length Ls on the extending direction on road), indicate the easness of the temperature change of cylinder body.That is, faced in cylinder body with suction passage
The surface area in region is bigger, and cylinder body is easier to be cooled down and temperature reduction by refrigerant.On the other hand, height of cylinder and suction passage
Extending direction on length it is bigger, since thermal capacity increases, center housing temperature is more not easy to reduce.In this way, logical with sucking in cylinder body
On extending direction of the temperature of the areas adjacent on road surface pair according to the surface area As in the region, height of cylinder Hp and suction passage
Length Ls three balance and change.
In Fig. 9, the approximate line A as straight line expression is the margin line of the performance limits in terms of indicating compressor efficiency.
That is, admissible compressor efficiency can be obtained is the region than approximate line A on the lower.In addition, identical as approximate line A as having
The straight line of slope come the approximate line B indicated be admissible (not adhering) margin line in terms of reliability.That is, not sending out
Raw adhesion is the region more top than approximate line B.Here,
Approximate line A are as follows:
(Hc-Hp)/Hc=1.4 × 0.0001 × As/ (HcLs)+6.7 × 0.0001,
Approximate line B are as follows:
(Hc-Hp)/Hc=1.4 × 0.0001 × As/ (HcLs)+3.9 × 0.0001.
Therefore, by making the value of aforementioned four parameter Hc, Hp, As, Ls meet relational expression
The value of 3.9 × 0.0001≤(Hc-Hp)/Hc-1.4 × 0.0001 × As/ (HcLs)≤6.7 × 0.0001,
So as to obtain meeting the compressor of compressor efficiency and reliability both sides.
[variation]
In above-mentioned first embodiment, it is also possible that the first cylinder body is lower cylinder body 50, the second cylinder body is upper cylinder body
30.That is, the surface area in the region faced in upper cylinder body 30 with suction passage might be less that in lower cylinder body 50 with suction passage face
Pair region surface area.Similarly, in this second embodiment, it is also possible that the first cylinder body is lower cylinder body 50, the second cylinder
Body is upper cylinder body 130.That is, the surface area in the region faced in upper cylinder body 130 with suction passage might be less that in lower cylinder body 50
The surface area in the region faced with suction passage.In addition, in the third embodiment, it is also possible that the first cylinder body is upper cylinder half
Body 230, the second cylinder body are lower cylinder body 250.That is, the surface area in the region faced in lower cylinder body 250 with suction passage can also be small
The surface area in the region faced in upper cylinder body 230 with suction passage.
The structure (configuration, cross sectional shape etc.) of suction passage is not limited to above-mentioned first to shown in third embodiment, can also
It changes as appropriate.As an example, first into third embodiment, exist to horizontal passageway 30a, 50a, 130a, 230a, 250a
The radially extending example of cylinder body is illustrated, as long as but these horizontal passageways be connected to discharge chambe, can also with drive
Extend in the orthogonal plane of the axial direction of moving axis to any direction.
First into third embodiment, as external equipment, instantiates and be fixed in rotary compression of the invention
The gas-liquid separator of machine, but not limited to this.External equipment is also possible to not be fixed in rotary compressor of the invention for example
Gas-liquid separator or gas-liquid separator other than equipment (evaporator etc.).
First into third embodiment, roller and the blade of piston are integrally formed, but roller can also be seperated with blade
Ground is constituted.
First into third embodiment, carried out to the rotary compressor of upper cylinder body and the twin-rotor housing of lower cylinder body
There are three but it is also possible to be tool with the rotary compressor of upper cylinder body for explanation.In this case, at three in upper cylinder body,
Preferably, the surface area in the region faced in the cylinder body with suction passage is smaller, the height in drive shaft axial direction of cylinder body
And the difference for being configured in the height in the axial direction of the piston of the discharge chambe of the cylinder body is smaller.
Embodiments of the present invention are illustrated above according to attached drawing, it is believed that specific structure is not limited to
These embodiments.The scope of the present invention is by claims rather than the explanation of above-mentioned embodiment indicates, also, wraps
It includes and all changes in the meaning and range of claims equalization.
Label declaration
1,201: rotary compressor
3: driving mechanism
4,204: compression mechanism
20,120: upper cover (end plate member)
30,130,230: upper cylinder body (cylinder body, the first cylinder body)
31,51: discharge chambe
32,52: piston
40,240: intermediate plate (end plate member)
50,250: lower cylinder body (cylinder body, the second cylinder body)
60: lower cover (end plate member)
Claims (6)
1. a kind of rotary compressor, accommodates compression mechanism and driving mechanism, the driving mechanism has to the compression
The drive shaft that mechanism is driven, the rotary compressor be characterized in that,
The compression mechanism has:
Multiple cylinder bodies, they are respectively formed with discharge chambe, and by the drive shaft be located at multiple compressions it is indoor in a manner of
It is arranged in the axial direction of the drive shaft；
Multiple end plate members, they are configured in the both ends in the axial direction of each cylinder body, and divide the discharge chambe；With
Multiple pistons, they are configured in the inside of each discharge chambe, are driven by the drive shaft,
The multiple cylinder body include the first cylinder body and the second cylinder body, second cylinder body across an end plate member and with institute
It is adjacent to state the first cylinder body,
It is formed with suction passage in the rotary compressor, the suction passage includes: the first access, will be from external equipment
It is provided via the refrigerant that suction line provides to the discharge chambe of first cylinder body；And alternate path, it is from described
The access of one forehearth limb, and refrigerant is provided to the discharge chambe of second cylinder body,
The surface area in the region faced in second cylinder body with the suction passage is less than in first cylinder body and the suction
Enter the surface area in the region that access faces,
The institute in the height in the axial direction and the discharge chambe for being configured in second cylinder body of second cylinder body
The difference in the height in the axial direction for stating piston is less than the height in the axial direction of first cylinder body and is configured in
The difference of the height in the axial direction of the piston in the discharge chambe of first cylinder body.
2. rotary compressor according to claim 1, which is characterized in that
First access passes through first cylinder body and does not pass through second cylinder body,
The alternate path in the inside of first cylinder body from first forehearth limb, by first cylinder body and described
Second cylinder body both sides.
3. rotary compressor according to claim 2, which is characterized in that
The suction line is configured to, can by its end be located at first cylinder it is intracorporal in a manner of be inserted into first cylinder
Body.
4. rotary compressor according to claim 2, which is characterized in that
The suction line is configured to, first cylinder body can be located relative to its end and configure with second cylinder body
Mode in the end plate member of opposite side is inserted into the end plate member.
5. rotary compressor according to any one of claims 1 to 4, which is characterized in that
In the multiple cylinder body, the surface area in the region faced in the cylinder body with the suction passage is smaller, the cylinder body
Height and the height in the axial direction for the piston being configured in the discharge chambe of the cylinder body in the axial direction
Difference it is smaller.
6. rotary compressor according to any one of claims 1 to 5, which is characterized in that
About any of the multiple cylinder body, if the height in the axial direction of the cylinder body is Hc (mm), sets and be configured
It is Hp (mm), sets the cylinder in the height in the axial direction of the piston of the inside for the discharge chambe for being formed in the cylinder body
The surface area in the region faced with the suction passage in body is As (mm2), set the suction passage in the cylinder body with
When length on the orthogonal direction of the axial direction is Ls (mm), meet:
3.9 × 0.0001≤(Hc-Hp)/Hc-1.4 × 0.0001 × As/ (HcLs)≤6.7 × 0.0001.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2017052710 | 2017-03-17 | ||
| JP2017-052710 | 2017-03-17 | ||
| PCT/JP2018/010583 WO2018169072A1 (en) | 2017-03-17 | 2018-03-16 | Rotary compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110418892A true CN110418892A (en) | 2019-11-05 |
| CN110418892B CN110418892B (en) | 2021-07-06 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201880017804.9A Active CN110418892B (en) | 2017-03-17 | 2018-03-16 | Rotary compressor |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP3597923B1 (en) |
| JP (1) | JP6787480B2 (en) |
| CN (1) | CN110418892B (en) |
| ES (1) | ES2953629T3 (en) |
| MY (1) | MY195534A (en) |
| WO (1) | WO2018169072A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110848140A (en) * | 2019-11-27 | 2020-02-28 | 广东美芝制冷设备有限公司 | Compressor air suction structure, compressor and refrigeration and heating equipment |
| CN114151339A (en) * | 2020-09-07 | 2022-03-08 | 沈阳中航机电三洋制冷设备有限公司 | Rotary compressor |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2020217385A1 (en) * | 2019-04-25 | 2020-10-29 | 三菱重工サーマルシステムズ株式会社 | Rotary compressor |
| DE102020117343A1 (en) * | 2020-07-01 | 2022-01-05 | Weinmann Emergency Medical Technology Gmbh + Co. Kg | Pump device, device for ventilation and method for providing a breathing gas |
| JP2024145222A (en) * | 2023-03-31 | 2024-10-15 | ダイキン工業株式会社 | 2 cylinder rotary compressor |
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| JPS6176790A (en) * | 1984-09-19 | 1986-04-19 | Sanyo Electric Co Ltd | Assembling of rotary compressor |
| JPS62195483A (en) * | 1986-02-21 | 1987-08-28 | Toshiba Corp | 2-cylinder type rotary compressor |
| JPH02218884A (en) * | 1989-02-21 | 1990-08-31 | Toshiba Corp | Multicylinder compressor |
| CN1295196A (en) * | 1999-11-04 | 2001-05-16 | 松下电器产业株式会社 | Enclosed rotary compressor |
| CN1620554A (en) * | 2001-12-20 | 2005-05-25 | Lg电子株式会社 | Suction mechanism of rotary compressor |
| CN1644926A (en) * | 2004-01-22 | 2005-07-27 | 三菱电机株式会社 | Double cylinder rotary compressor |
| JP2009062929A (en) * | 2007-09-07 | 2009-03-26 | Toshiba Carrier Corp | Rotary compressor and refrigerating cycle device |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6112104B2 (en) | 2014-12-19 | 2017-04-12 | 株式会社富士通ゼネラル | Rotary compressor |
-
2018
- 2018-03-16 WO PCT/JP2018/010583 patent/WO2018169072A1/en active Application Filing
- 2018-03-16 MY MYPI2019005092A patent/MY195534A/en unknown
- 2018-03-16 EP EP18767860.2A patent/EP3597923B1/en active Active
- 2018-03-16 CN CN201880017804.9A patent/CN110418892B/en active Active
- 2018-03-16 ES ES18767860T patent/ES2953629T3/en active Active
- 2018-03-16 JP JP2019506315A patent/JP6787480B2/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6176790A (en) * | 1984-09-19 | 1986-04-19 | Sanyo Electric Co Ltd | Assembling of rotary compressor |
| JPS62195483A (en) * | 1986-02-21 | 1987-08-28 | Toshiba Corp | 2-cylinder type rotary compressor |
| JPH02218884A (en) * | 1989-02-21 | 1990-08-31 | Toshiba Corp | Multicylinder compressor |
| CN1295196A (en) * | 1999-11-04 | 2001-05-16 | 松下电器产业株式会社 | Enclosed rotary compressor |
| CN1620554A (en) * | 2001-12-20 | 2005-05-25 | Lg电子株式会社 | Suction mechanism of rotary compressor |
| CN1644926A (en) * | 2004-01-22 | 2005-07-27 | 三菱电机株式会社 | Double cylinder rotary compressor |
| JP2009062929A (en) * | 2007-09-07 | 2009-03-26 | Toshiba Carrier Corp | Rotary compressor and refrigerating cycle device |
| CN102644597A (en) * | 2011-02-16 | 2012-08-22 | 广东美芝制冷设备有限公司 | Double-cylinder rotary compressor |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110848140A (en) * | 2019-11-27 | 2020-02-28 | 广东美芝制冷设备有限公司 | Compressor air suction structure, compressor and refrigeration and heating equipment |
| CN114151339A (en) * | 2020-09-07 | 2022-03-08 | 沈阳中航机电三洋制冷设备有限公司 | Rotary compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| EP3597923B1 (en) | 2023-05-31 |
| EP3597923A4 (en) | 2021-01-20 |
| EP3597923A1 (en) | 2020-01-22 |
| WO2018169072A1 (en) | 2018-09-20 |
| JP6787480B2 (en) | 2020-11-18 |
| MY195534A (en) | 2023-01-31 |
| CN110418892B (en) | 2021-07-06 |
| JPWO2018169072A1 (en) | 2019-12-12 |
| ES2953629T3 (en) | 2023-11-14 |
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