CN107532597B - Cylinder revolution type compressor - Google Patents

Cylinder revolution type compressor Download PDF

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Publication number
CN107532597B
CN107532597B CN201680018336.8A CN201680018336A CN107532597B CN 107532597 B CN107532597 B CN 107532597B CN 201680018336 A CN201680018336 A CN 201680018336A CN 107532597 B CN107532597 B CN 107532597B
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CN
China
Prior art keywords
rotor
cylinder
discharge chambe
axis
side plate
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Expired - Fee Related
Application number
CN201680018336.8A
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Chinese (zh)
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CN107532597A (en
Inventor
大野雄一
小川博史
内田和秀
村濑善则
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Denso Corp
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Denso Corp
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Expired - Fee Related legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • 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
    • 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
    • F04C18/344—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 inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C18/344—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 inner member
    • F04C18/3441—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 inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C18/3442—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 inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the inlet and outlet opening
    • 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
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/18—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber
    • F04C28/22—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • 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
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/0085—Prime movers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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
    • F04C18/332—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 inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C18/332—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 inner member
    • F04C18/336—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 inner member and hinged to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • 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
    • F04C2240/60—Shafts
    • 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
    • F04C2240/60—Shafts
    • F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft

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

Abstract

Cylinder revolution type compressor has: around the cylindric cylinder (21) of central axis (C1) rotation；Around the cylindric the first rotor (22a) and the second rotor (22b) of eccentric shaft (C2) rotation, eccentric shaft (C2) is eccentric relative to the central axis (C1) of cylinder (21)；Axis (24)；First blade (23a)；Second blade (23b).First blade (23a) is embedded into the first groove portion (222a) for being formed in the first rotor (22a) in a manner of it can slide, and separates the first discharge chambe (Va).Second blade (23b) is embedded into the second groove portion (222b) for being formed in the second rotor (22b) in a manner of it can slide, and separates the second discharge chambe (Vb).The first rotor (22a) and the second rotor (22b) are configured to arrange on direction central axis (C1) of cylinder (21).

Description

Cylinder revolution type compressor
The mutual reference of related application
The application quotes its note based on Japanese patent application 2015-66056 proposed on March 27th, 2015 herein Carry content.
Technical field
The present invention relates to a kind of cylinder revolution type compressors made in the internal cylinder rotation for forming discharge chambe.
Background technique
Conventionally, there is known such cylinder revolution type compressor: making in the internal cylinder rotation for forming discharge chambe, to make The volume of discharge chambe changes and compresses and fluid is discharged.
For example, patent document 1 discloses a kind of cylinder revolution type compressor, which includes: (electronic with motor part Motor part) the cylindric cylinder that is integrally formed of rotor；It is configured at the cylindric rotor of the inside of cylinder；The leaf of plate Piece, the blade are embedded in the groove portion (slit portion) for being formed in rotor in a manner of it can slide and separate discharge chambe.
In this cylinder revolution type compressor, make cylinder and rotor with different rotary shaft linkage rotations, to make Blade displacement changes the volume of discharge chambe.In addition, in the cylinder revolution type compressor of patent document 1, by compression mechanical part It is configured at the inner circumferential side of motor part, to realize the miniaturization of compressor entirety.
Existing technical literature
Patent document
Patent document 1: Japanese Unexamined Patent Publication 2012-67735 bulletin
The summary of invention
However, the increased means of discharge ability as the cylinder revolution type compressor for making patent document 1, it is contemplated that make The outer diameter (internal diameter of cylinder) of discharge chambe expands, to make capacity (discharge capacity) widened means of discharge chambe.
However, being configured at the electricity of the peripheral side of cylinder if expanding the internal diameter of cylinder to increase discharge ability The outer diameter in motivation portion also expands, to be difficult to obtain the miniaturization effect of above-mentioned compressor entirety.In addition, if making that capacity is discharged Expand, then cogging when compressor is run also increases, to become the noise for making compressor entirety, the increased original of vibration Cause.
Summary of the invention
The purpose of the present invention is to provide a kind of cylinder revolution type compressor, which can expand pressure The capacity of contracting room is without leading to radial enlargement.
In one embodiment of the present invention, cylinder revolution type compressor has: around the cylindric gas of center axis rotation Cylinder；The cylindric the first rotor and the second rotor rotated around eccentric shaft, eccentricity of central axis of the eccentric shaft relative to cylinder； It is the axis that can be rotated by the first rotor and the second rotor bearing；First blade, first blade is in a manner of it can slide It is embedded into the first groove portion for being formed in the first rotor, and separates the first discharge chambe, which is formed in the first rotor Between outer peripheral surface and the inner peripheral surface of cylinder；Second blade, which is embedded into a manner of it can slide is formed in second Second groove portion of rotor, and separate the second discharge chambe, which is formed in the interior of bitrochanteric outer peripheral surface and cylinder Between circumferential surface.The first rotor and the second rotor configuration are arranged on the direction of the central axis of cylinder.It is formed in the inside of axis There is axis side suction passage, axis side suction passage will be oriented to the first discharge chambe and the second compression from the compressed object fluid of outside sucking Room is formed with first axle side outlet hole and the second axis side outlet hole in the outer peripheral surface of axis, and the first axle side outlet hole side Shi Zhou is inhaled The compressed object fluid for entering access circulation is flowed out to the first discharge chambe, and the second axis side outlet hole makes in the circulation of axis side suction passage Compressed object fluid is flowed out to the second discharge chambe, the first discharge chambe and the second discharge chambe relative to compressed object fluid flowing and It connects side by side
As a result, due to having the first rotor and the second rotor, it is capable of forming the first discharge chambe and the second compression Room.Therefore, the total capacity (capacity is always discharged) of the first discharge chambe and the second discharge chambe can easily be expanded.In addition, first turn Son and the second rotor configuration are arranged on the central axis direction of cylinder, therefore can expand total discharge capacity without expanding gas The outer diameter of cylinder.
As a result, be capable of providing a kind of cylinder revolution type compressor, the compressor can expand the capacity of discharge chambe and Radial enlargement is not caused.
In addition, the eccentric shaft and bitrochanteric eccentric shaft of the first rotor can also be configured on coaxial.Do not have as a result, Necessity forms the position with different eccentric axis in axis, is able to easily form axis.
In addition it is also possible to be: the rotation angle and second of cylinder when the first indoor Fluid pressure of compression reaches maximum pressure The rotation angle for compressing cylinder when indoor Fluid pressure reaches maximum pressure differs 180 °.Thereby, it is possible to inhibit to compress because expanding The increase of torque fluctuation caused by the capacity of room can effectively inhibit the noise of compressor entirety, the increase of vibration.
Also, " 180 ° of difference " not merely indicates fully to differ 180 °, also illustrates that due to manufacturing upper or fit on Error and opposite 180 ° have the case where tiny error.
Detailed description of the invention
Above-mentioned and other purposes of the invention, feature, advantage while referring to attached drawing by carrying out following descriptions And definitely.
Fig. 1 is the axial sectional view of the compressor of first embodiment.
Fig. 2 is the II-II cross-sectional view of Fig. 1.
Fig. 3 is the III-III cross-sectional view of Fig. 1.
Fig. 4 is the exploded perspective view of the compression mechanical part of the compressor of first embodiment.
Fig. 5 is the explanatory diagram for illustrating the operating status of compressor of first embodiment.
Fig. 6 is the chart for indicating the cogging of compressor of first embodiment.
Fig. 7 is that the axial sectional view of the compressor of second embodiment and Fig. 3 are corresponded to.
Fig. 8 is that the axial sectional view of the compressor of third embodiment and Fig. 3 are corresponded to.
Specific embodiment
(first embodiment)
In the following, illustrating first embodiment with attached drawing.(the following brief note of cylinder revolution type compressor 1 of present embodiment For compressor 1) suitable for carrying out cooling both vapor compression to being blown into the indoor wind pushing air of vehicle air conditioner for vehicles The refrigerating circulatory device of formula plays compressed object fluid i.e. refrigerant compression and the function of discharge in the refrigerating circulatory device Energy.
In addition, in the refrigerating circulatory device, using HFC series coolant (specifically R134a) as refrigerant, And constitute subcritical refrigeration cycle of the high-pressure side refrigerant pressure no more than the critical pressure of refrigerant.In addition, being mixed in refrigerant Enter the lubricating oil i.e. refrigerating machine oil for thering is the sliding position to compressor 1 to be lubricated, a part and refrigerant one of refrigerating machine oil It rises and recycles in the circulating cycle.
As shown in Figure 1, compressor 1 is configured to motor compressor, which is forming shell of motor compressor The inside of shell 10 accommodates: by refrigerant compression and the compression mechanical part 20 of discharge, and driving the electronic of compression mechanical part 20 Machine portion (electric motor portion) 30.Also, compressor 1 is being equipped on air conditioner for vehicles by the arrow each up and down expression in Fig. 1 In the state of all directions up and down.
Firstly, shell 10 is constituted by combining multiple metal parts, it is to form substantial cylindrical space internal Closed container structure.
More specifically, as shown in Figure 1, shell 10 is constituted by combining with lower component: bottomed cylindrical (cup-shaped) Main casing 11；It is configured to the sub-shell 12 of the bottomed cylindrical of the opening portion of closing main casing 11；And it is configured to closing subshell The disk-shaped cover 13 of the opening portion of body 12.
Also, there are the not shown of the compositions such as O-ring in the abutting part of main casing 11, sub-shell 12 and cover 13 Seal member, refrigerant will not leak out from each abutting part.
In the tubular side of main casing 11 it is formed with outlet 11a, outlet 11a will be boosted in compression mechanical part 20 High-pressure refrigerant is discharged to the outside (specifically, being the refrigerant inlet side of the condenser of refrigerating circulatory device) of shell 10. It is formed with suction inlet 12a in the tubular side of sub-shell 12, suction inlet 12a is by low pressure refrigerant (specifically, being followed from refrigeration The low pressure refrigerant of the evaporator outflow of loop device) it is sucked from the external of shell 10.
Shell side suction passage 13a is formed between sub-shell 12 and cover, shell side suction passage 13a is used for will The low pressure refrigerant sucked from suction inlet 12a imported into the first discharge chambe Va of compression mechanical part 20, the second discharge chambe Vb.This Outside, it is equipped in the face of the side opposite with the face of 12 side of sub-shell of cover 13 and feeds electrical power to the drive of motor part 30 Dynamic circuit (inverter) 30a.
Motor part 30 has the stator 31 as stator.Stator 31 has the stator core formed by metallicl magnetic material The 31a and stator coil 31b for being wound in stator core 31a is fixed on main casing by means such as indentation, hot charging, bolt fastenings The inner peripheral surface of the tubular side of body 11.
If electric power is supplied to stator coil 31b through not shown hermetic terminal (airtight terminal) from driving circuit 30a, Rotating excitation field is then generated, which rotate the cylinder 21 for being configured at the inner circumferential side of stator 31.Cylinder 21 is by cylindrical shape Metallicl magnetic material is formed, and as described later, cylinder 21 forms the first discharge chambe Va, the second discharge chambe Vb of compression mechanical part 20.
As shown in the cross-sectional view of Fig. 2, Fig. 3, magnet (permanent magnet) 32 is fixed at cylinder 21.Cylinder 21 has both as a result, The function of rotor as motor part 30.Then, cylinder 21 is revolved using the rotating excitation field that stator 31 generates around central axis C1 Turn.
That is, in the compressor 1 of present embodiment, the rotor of motor part 30 and the cylinder of compression mechanical part 20 21 are constituted to be integrally constituted.The rotor of motor part 30 and the cylinder 21 of compression mechanical part 20 can also be constituted with other component, And make 21 integration of cylinder of the rotor and compression mechanical part 20 of motor part 30 by means such as indentations.In addition, motor part 30 stator (stator core 31a and stator core 31b) is configured at the peripheral side of cylinder 21.
Then, compression mechanical part 20 is illustrated.In the present embodiment, as compression mechanical part 20, it is equipped with first Compression mechanical part 20a and the second compression mechanical part 20b the two.First compression mechanical part 20a, the second compression mechanical part 20b Basic structure it is mutually equal.In addition, the first compression mechanical part 20a, the second compression mechanical part 20b are opposite in the inside of shell 10 Refrigerant stream and connect side by side.
As shown in Figure 1, the first compression mechanical part 20a, the second compression mechanical part 20b are arranged on the central axis direction of cylinder 21 Column configuration.Herein, in the present embodiment, by the conduct of the bottom surface side for being configured at main casing 11 in two compression mechanical parts One compression mechanical part 20a will be configured at the second compression mechanical part of conduct 20b of 12 side of sub-shell.
In addition, in Fig. 1, Fig. 4, in the component parts of the second compression mechanical part 20b with the first compression mechanism 20a The letter at end is altered to " b " from " a " by the corresponding symbol of same component parts.For example, for the second compression mechanical part I.e. the second rotor of component parts corresponding with the first rotor 22a of the first compression mechanical part 20a in the component parts of 20a, It is labeled as " 22b ".
First compression mechanical part 20a includes cylinder 21, the first rotor 22a, the first blade 23a, axis 24 etc..Second compression Mechanism part 20b includes cylinder 21, the second rotor 22b, the second blade 23b, axis 24 etc..That is, as shown in Figure 1, in cylinder 21 and axis 24 in, the bottom surface side of main casing 11 a part constitute the first compression mechanical part 20a, another portion of 12 side of sub-shell Divide and constitutes the second compression mechanical part 20b.
As previously mentioned, cylinder 21 is cylinder-like part, as motor part 30 rotor and rotated around central axis C1, and In the second discharge chambe Vb of internal the first discharge chambe Va and the second compression mechanical part 20b for forming the first compression mechanical part 20a. In the circumferential one end of cylinder 21, the means such as it is fastened by bolts and is fixed with the closing portion of the open end of closed cylinder 21 Part i.e. the first side plate 25a.In addition, being similarly fixed with the second side plate 25b in the axial another side of cylinder 21.
First side plate 25a, the second side plate 25b have the circle extended in the rotary shaft generally perpendicular direction with cylinder 21 Plate-like portion and the central part and flange part outstanding in the axial direction for being configured at disk-shaped portion.In addition, being formed with perforation in flange part The inside and outside through hole of first, second side plate 25a, 25b.
Bearning mechanism (not shown) is each configured in these through holes, in the Bearning mechanism inserted with axis 24, thus Cylinder 21 is supported to rotate freely relative to axis 24.The both ends of axis 24 are individually fixed in shell 10 (specifically, being main casing Body 11 and side body 12).Therefore, axis 24 will not be rotated relative to shell 10.
The cylinder 21 of present embodiment is formed with the first discharge chambe Va and the second discharge chambe demarcated mutually in inside Vb.Therefore, between the first rotor 22a and the second rotor 22b of the inside of cylinder 21, configured with for dividing the first discharge chambe The disk-shaped intermediate side plate 25c of Va and the second discharge chambe Vb.The intermediate side plate 25c also have with the first side plate 25a, second Side plate 25b the same function.
That is, the axial ends at the position of the first compression mechanical part of composition 20a in the cylinder 21 of present embodiment It is closed by the first side plate 25a and centre side plate 25c in portion.In addition, the portion of the second compression mechanical part of composition 20b in cylinder 21 The axial ends portion of position is closed by the second side plate 25b and centre side plate 25c.
In other words, the first side plate 25a and intermediate side plate 25c, the first rotor 22a etc. mark off the first discharge chambe Va together, Second side plate 25b and intermediate side plate 25c, the second rotor 22b etc. mark off the second discharge chambe Vb together.In addition, intermediate side plate 25c It is configured between the first rotor 22a and the second rotor 22b, and divides the first discharge chambe Va and the second discharge chambe Vb.
Also, in the present embodiment, cylinder 21 and centre side plate 25c are integrally formed, but can also use different component structures At cylinder 21 and intermediate side plate 25c, and make their integrations by means such as indentations.In addition, in the present embodiment, dividing Are as follows: the axial length of the axial length of the first rotor 22a and the second rotor 22b are identical, the pressure of the first discharge chambe Va and second The contracting room respective maximum volume of Vb is substantially mutually identical.
Axis 24 is substantially cylindric component, by cylinder 21 (specifically, be affixed to each side plate 25a of cylinder 21, 25b, 25c), the first rotor 22a and the second rotor 22b rotatably support.
In the axial central portion of axis 24, the eccentric part 24c of the end of 12 side of sub-shell is less than equipped with outer diameter.The bias The central axis of portion 24c is the eccentric shaft C2 of the central axis C1 bias relative to cylinder 21.In addition, in eccentric part 24c, via not scheming The Bearning mechanism that shows and the first rotor 22a, the second rotor 22b are rotatably supported.
As previously mentioned, the first compression mechanical part 20a of present embodiment, the second compression mechanical part 20b are in cylinder 21 Mandrel is arranged on direction.Accordingly, with respect to the first rotor 22a and the second rotor 22b, as Figure 1 and Figure 4, also in rotor It is arranged on 21 central axis direction.In addition, when the first rotor 22a, the second rotor 22b rotate, the first rotor 22a, second Rotor 22b is rotated around common eccentric shaft C2, and eccentric shaft C2 is eccentric relative to the central axis C1 of cylinder 21.That is, at this In embodiment, the eccentric shaft of the eccentric shaft of the first rotor 22a and the second rotor 22b are configured on coaxial.
As shown in Figure 1, being formed with axis side suction passage 24d in the inside of axis 24, the axis side suction passage 24d is for connecting Logical shell side suction passage 13a, and the low pressure refrigerant flowed into from outside is imported into the first discharge chambe Va, the second discharge chambe Vb Side.There are multiple (being four in the present embodiment) first axle side outlet hole 240a, the second axis side in the outer peripheral surface opening of axis 24 Outlet opening 240b makes the low pressure refrigerant outflow for circulating in axis side suction passage 24d.
As Figure 1 and Figure 4, in the outer peripheral surface of axis 24, it is formed with the first axle for making the inward-facing side recess in the periphery of axis 24 Side pocket 241a, the second axis side pocket 241b.Then, first axle side outlet hole 240a, the second axis side outlet hole 240b exist respectively It is formed with the position opening of first axle side pocket 241a, the second axis side pocket 241b.Therefore, first axle side outlet hole 240a, Circular first of two axis side outlet hole 240b and the inside for being formed in first axle side pocket 241a, the second axis side pocket 241b Axis side connects universal space 242a, the second axis side connects universal space 242b connection.
The first rotor 22a is cylinder-like part, is configured at the inside of cylinder 21, and prolong in the central axis direction of cylinder 21 It stretches.As shown in Figure 1, the axial length of the first rotor 22a is formed as the first compression mechanical part with composition axis 24 and cylinder 21 The roughly equal size of the axial length at the position of 20a.
In addition, the outer diameter of the first rotor 22a is formed as less than the cylindrical space for being formed in the inside of cylinder 21 Internal diameter.In more detail, as shown in Figure 2 and Figure 3, the outer diameter setting of the first rotor 22a are as follows: from the axis of eccentric shaft C2 To when observation, the outer peripheral surface of the first rotor 22a and the inner peripheral surface of cylinder 21 are contacted in a contact point C3.
Between the first rotor 22a and intermediate side plate 25c and between the first rotor 22a and the first side plate 25a, it is configured with Transmission mechanism.Transmission mechanism is by rotary driving force from (the intermediate side plate more specifically rotated together with cylinder 21 of cylinder 21 25c and the first side plate 25a) it is transmitted to the first rotor 22a, so that 21 synchronous rotary of the first rotor 22a and cylinder.
It is illustrated by taking the transmission mechanism being configured between the first rotor 22a and intermediate side plate 25c as an example.As shown in Fig. 2, Multiple (being four in present embodiment) that transmission mechanism includes the face for being formed in the side intermediate plate 25c of the first rotor 22a are round First hole portion 221a of shape；And multiple (these outstanding on central axis direction from intermediate side plate 25c to the side the first rotor 22a It is four in embodiment) drive pin 251c.
These drive pins 251c is formed as path of the diameter less than the diameter of the first hole portion 221a, and towards 22 pleurapophysis of rotor Out, it is respectively embedded into the first hole portion 221a.Therefore, drive pin 251c and the first hole portion 221a composition is equal to so-called pin hole formula The mechanism of the anti-locking mechanism of rotation.Transmission mechanism between the first rotor 22a and the first side plate 25a also has same structure.
Transmission mechanism according to the present embodiment, when cylinder 21 is rotated around central axis C1, then each drive pin 251c and axis 24 The relative position (relative distance) of eccentric part 24c change.The variation of (relative distance) depending on the relative position, first turn The side wall surface of the first hole portion 221a of sub- 22a receives the loading of direction of rotation from drive pin 251c.As a result, the first rotor 22a is synchronous with the rotation of cylinder 21 and rotates around eccentric shaft C2.
Herein, in the transmission mechanism of present embodiment, sequentially from multiple drive pin 251c and the first hole portion 221a to Rotor 22 transmits power.It is preferred, therefore, that multiple drive pin 251c and the first hole portion 221a be configured to be with eccentric shaft C2 The center of circle and keep equiangularly spaced.In addition, being embedded with metal ring component 223a, ring portion in each first hole portion 221a The abrasion for the inner circumferential side wall surface that part 223a is used to inhibit to contact with drive pin 251c.
In addition, as indicated by the dashed line in figure 1, in the inside of the first rotor 22, being formed with the first oily access 225a, the first oil is logical Axis of the road 225a in eccentric shaft C2 upwardly extends, and penetrates into another side from the axial direction one end.
First oil access 225a is made via the first way to cycle oil 11b of the bottom surface side for being formed in main casing 11 and formation In the lubricating oil for the refrigerating machine oil circulation that the oily access 252a in the gap of axis 24 and the flange part of the first side plate 25a etc. is supplied to Access.First way to cycle oil 11b is that the refrigerating machine oil of the lower side for the inner space for being stored in shell 10 is imported into the first oil The oil passage of the side access 225a.
In addition, being set between the first rotor 22a and intermediate side plate 25c and being set to the first rotor 22a and the first side plate 25a Between the first hole portion 221a of transmission mechanism formed respectively by the axial ends portion of the first oily access 225a.
In other words, at least one first hole portion of the transmission mechanism between the first rotor 22a and the first side plate 25a with And at least one first hole portion 221a of the transmission mechanism between the first rotor 22a and intermediate side plate 25c is via the first oil Access 225a and interconnect.
In addition, as shown in Figure 2 and Figure 3, being formed in axial full scope inwardly in the outer peripheral surface of the first rotor 22a The first groove portion (the first slit portion) 222a of side recess.Aftermentioned first blade 23a is embedded in a manner of it can slide One groove portion 222a.
When from the end on observation of eccentric shaft C2, the face of confession the first blade 23a sliding of the first groove portion 222a is (with the first blade The rubbing surface of 23a) opposite the first rotor 22a radial skew.More specifically, the first blade 23a of confession of the first groove portion 222a The face of sliding is tilted from inner circumferential side towards periphery side to direction of rotation.Therefore, it is embedded in the first blade 23a of the first groove portion 222a Also it is displaced to the direction of the radial skew relative to the first rotor 22a.
As shown in figure 3, the axial central portion in the first rotor 22a is formed with the first rotor side suction passage 224a, this One rotor side suction passage 224a and the first groove portion 222a is the same relative to radial skew extends, and make the first rotor 22a's Inner circumferential side (first axle side connects the side universal space 242a) is connected to peripheral side (the first side discharge chambe Va).It is flowed into as a result, from outside Refrigerant to axis side suction passage 24d is directed to the side the first rotor side suction passage 224a.
In addition, as shown in figure 3, the outlet opening of the first rotor side suction passage 224a is located to relative to the first groove portion 222a The outer peripheral surface of the first rotor 22a of direction of rotation rear side is open.In addition, the first rotor side suction passage 224a and the first slot Portion 222a is demarcated mutually, is formed as respective inner space and is not connected to.
First blade 23a is by the partition member of the first discharge chambe Va plate separated, and the first discharge chambe Va is formed in the Between the outer peripheral surface of one rotor 22a and the inner peripheral surface of cylinder 21.The axial length of first blade 23a is formed as and the first rotor The axial length of 22a is roughly the same.In addition, the peripheral side top end part of the first blade 23a is configured to the interior of opposite cylinder 21 Circumferential surface sliding.
Therefore, in the first compression mechanical part 20a of present embodiment, the first discharge chambe Va by cylinder 21 inner wall, The space shape that the outer peripheral surface of the first rotor 22a, the plate face of the first blade 23a, the first side plate 25a, centre side plate 25c are surrounded At.That is, the first blade 23a is separated to form between the inner peripheral surface of cylinder 21 and the outer peripheral surface of the first rotor 22a One discharge chambe Va.
In addition, being formed with the first tap 251a in the first side plate 25a, which makes by the first discharge chambe Va compression Refrigerant is discharged to the inner space of shell 10.In addition, being configured with the first discharge being made of pilot valve in the first side plate 25a Valve, the pilot valve inhibit the refrigerant for flowing out to the inner space of shell 10 from the first tap 251a via the first tap 251a is countercurrently to the first discharge chambe Va.
Then, the second compression mechanical part 20 is illustrated.As previously mentioned, the basic structure of the second compression mechanical part 20b As the first compression mechanical part 20a.Therefore, as shown in Figure 1, the second rotor 22b is cylinder-like part, the second rotor 22b's Axial length is formed as roughly equal with the axial length at the position for the second compression mechanical part 20b for constituting axis 24 and cylinder 21 Size.
In addition, the eccentric shaft C2 of the eccentric shaft C2 and the first rotor 22a of the second rotor 22b is configured on coaxial, therefore from When the end on observation of eccentric shaft C2 as the first rotor 22a, the outer peripheral surface of the second rotor 22b and the inner peripheral surface of cylinder 21 exist It is contacted at contact point C3 as shown in Figure 2 and Figure 3.
Between the second rotor 22b and intermediate side plate 25c, and between the second rotor 22b and the first side plate 25a, if There is the transmission mechanism as the conduction mechanism to the first rotor 22a transmitting rotary driving force.Therefore, in the second rotor 22b shape At the second hole portion for having multiple rounds for multiple drive pin 251c insertion.It is also embedded with and the first hole portion in second hole portion 221a the same ring component.
In addition, from intermediate side plate 25c to the second side rotor 22b drive pin 25c outstanding with from intermediate side plate 25c to first The side rotor 22a drive pin 251c outstanding is formed by the same part.That is, being fixed on the drive pin of intermediate side plate 25c 251c is prominent on central axis direction towards the side the first rotor 22a and the second rotor 22b side both sides.
As shown in Figure 1, being formed with the first of the second oil access 225b and the first rotor 22a in the inside of the second rotor 22b Oily access 225a is the same, and axis of the second oil access 225b in eccentric shaft C2 upwardly extends, and penetrates into separately from the axial direction one end One end.
Second oil access 225b is to make via the second way to cycle oil 12b for being formed in sub-shell 12 and be formed in 24 He of axis What the oily access 252b in the gap of the flange part of the second side plate 25b etc. was supplied to makes the oil passage of refrigerating machine oil circulation.The Two way to cycle oil 12b are that the refrigerating machine oil of the lower side for the inner space for being stored in shell 10 is imported into the second oily access 225b The oil passage of side.
In addition, as the first oily access 225a, the axial ends portion of the second oily access 225b forms the of transmission mechanism Two hole portions.
In addition, being formed in the outer peripheral surface of the second rotor 22b in axial full scope as shown in the dotted line of Fig. 2, Fig. 3 Interior the second groove portion (the second slit portion) 222b being recessed to inner circumferential side.As the first blade 23a of the first groove portion 222a, second Blade 23b is embedded in the second groove portion 222b in a manner of it can slide.
As is shown in phantom in fig. 3, the sucking of the second rotor-side is formed in the inside of the axial central portion of the second rotor 22b to lead to Road 224b, the second rotor side suction passage 224b and the second groove portion 222b is the same relative to radial skew extends, and make The inner circumferential side of two rotor 22b is connected to peripheral side (the second side discharge chambe Vb).
Therefore, in the second compression mechanical part 20b of present embodiment, the second discharge chambe Vb by cylinder 21 inner wall, The space shape that the outer peripheral surface of second rotor 22b, the plate face of the second blade 23b, the second side plate 25b, centre side plate 25c are surrounded At.That is, the second blade 23b is separated to form between the inner peripheral surface of cylinder 21 and the outer peripheral surface of the second rotor 22b Two discharge chambe Vb.
In addition, being formed with the second tap 251b in the second side plate 25b, second tap 251b makes by the second discharge chambe The refrigerant of Vb compression is discharged to the inner space of shell 10.In addition, being configured with the be made of pilot valve in the second side plate 25b Two dump valves, the pilot valve inhibit the refrigerant for flowing out to the inner space of shell 10 from the second tap 251b via second row The 251b that portals is countercurrently to the second discharge chambe Vb.
In addition, as shown in Figure 2 and Figure 3, in the second compression mechanical part 20b of present embodiment, the second blade 23b, second First leaf relative to the first compression mechanism 20a such as second tap 251b of rotor side suction passage 224b, the second side plate 25b It is configured at for first tap 251a of piece 23a, the first rotor side suction passage 224a, the first side plate 25a etc. and substantially differs The position of 180 ° of phases.
Then, it is illustrated with Fig. 5 come the operation of the compressor 1 to present embodiment.Fig. 5 is in order to illustrate compressor 1 Operating status and continuously indicate with cylinder 21 rotation the first discharge chambe Va variation explanatory diagram.
That is, indicated by the solid line and Fig. 3 is same in the cross-sectional view corresponding with each rotation angle θ of cylinder 21 of Fig. 5 Cross-sectional view in the first rotor side suction passage 224a and the first blade 23a etc. position.In addition, in Fig. 5, with void Line indicates the position of the second rotor side suction passage 224b and the second blade 23b under each rotation angle θ.In addition, in Fig. 5, In order to keep diagram clear, the symbol of each component parts is marked in cross-sectional view corresponding with rotation angle θ=0 ° of cylinder 21.
Firstly, contact point C3 is overlapped with the peripheral side top end part of the first blade 23a when rotation angle θ is 0 °.In the state Under, the first discharge chambe Va of maximum volume is formed in the direction of rotation front side of the first blade 23a, and in the first blade 23a Direction of rotation rear side, be also formed with the first discharge chambe Va of the induction stroke of minimum volume (i.e. volume be 0).
Herein, the first discharge chambe Va of induction stroke is indicated in the first discharge chambe Va made in the stroke of volume enlargement, First discharge chambe Va of compression stroke is indicated in the first discharge chambe Va made in the stroke of smaller volume.
In addition, with rotation angle θ from 0 ° increase, as shown in rotation angle θ=45 °~315 ° of Fig. 5,21, first turns of cylinder Sub- 22a and the first blade 23a displacement, to be formed in the of the induction stroke of the direction of rotation rear side of the first blade 23a The volume of one discharge chambe Va increases.
As a result, from be formed in sub-shell 12 suction inlet 12a suck low pressure refrigerant with shell side suction passage 13a → First axle side outlet hole 240a → the first rotor side suction passage 224a sequential flowing of axis side suction passage 24d, and flow into Into the first discharge chambe Va of induction stroke.
At this point, because of the effect of the centrifugal force of the rotation with rotor 22, the first blade 23a's is outer at the first blade 23a Side top end part is pressed into the inner peripheral surface of cylinder 21.As a result, the first blade 23a divide induction stroke the first discharge chambe Va and First discharge chambe Va of compression stroke.
Then, when rotation angle θ reaches 360 ° (that is, when the states for returning to rotation angle θ=0 °), then the first of induction stroke is pressed Contracting room Va is maximum volume.In addition, then at rotation angle θ=0 °~360 °, volume is increased when rotation angle θ increases from 360 ° Induction stroke the first discharge chambe Va and the first rotor side suction passage 224a between connection be blocked.As a result, first The direction of rotation front side of blade 23a forms the first discharge chambe Va of compression stroke.
In addition, with rotation angle θ from 360 ° increase, as Fig. 5 rotation angle θ=405 °~675 ° in point shade institute part It is shown, it is formed in the smaller volume of the first discharge chambe Va of the compression stroke of the direction of rotation front side of the first blade 23a.
The refrigerant pressure in the first discharge chambe Va of compression stroke rises as a result,.Then, if in the first discharge chambe Va Refrigerant pressure be more than based on the refrigerant pressure in the inner space of shell 10 and the valve opening pressure of the first dump valve of determination (i.e. The maximum pressure of first discharge chambe Va), then the refrigerant in the first discharge chambe Va is discharged to shell via the first tap 251a The inner space of body 10.
In addition, in above-mentioned operation explanation, in order to keep the method for operation of the first compression mechanical part 20a more clear, explanation Rotation angle θ change between 0 ° to 720 ° during the first discharge chambe Va variation, but in fact, arrived in rotation angle θ at 0 ° When changing between 360 ° the compression stroke of illustrated refrigerant and when rotation angle θ changes between 360 ° to 720 ° it is illustrated Refrigerant compression stroke cylinder 21 once rotate when carry out simultaneously.
In addition, the second compression mechanical part 20b is similarly run, to carry out the compression and sucking of refrigerant.At this point, In the second compression mechanical part 20b, second blade 23b etc. is for first blade 23a of the first compression mechanical part 20a etc. It is configured at the position of 180 ° of phases of difference.Therefore, in the second discharge chambe Vb of compression stroke, relative to the first discharge chambe Va It differs the rotation angle of 180 ° of phases and carries out the compression and sucking of refrigerant.
Therefore, in the present embodiment, cylinder 21 when the refrigerant pressure in the first discharge chambe Va reaches maximum pressure The rotation angle θ of cylinder 21 also differs 180 ° when refrigerant pressure in rotation angle θ and the second discharge chambe Vb reaches maximum pressure.
Then, the refrigerant pressure in the second discharge chambe Vb of compression stroke rises, if the refrigeration in the second discharge chambe Vb Agent pressure is more than to be configured at the valve opening pressure (that is, maximum pressure of the second discharge chambe Vb) of the second dump valve of the second side plate 25b, then Refrigerant in second discharge chambe Vb discharge the inner space of shell 10 via the second tap 251b.From the second compressor The refrigerant interflow that structure portion 20b is discharged to the refrigerant of the inner space of shell 10 and is discharged from the first compression mechanical part 20a.
From the height the first compression mechanical part 20a the high pressure vapor refrigerant being discharged and be discharged from the second compression mechanical part 20b The interflow refrigerant of pressure vapor phase refrigerant reduces flow velocity in the inner space of shell 10.As a result, with high pressure vapor refrigerant Lower side is fallen under gravity from the refrigerating machine oil that the first tap 251a, the second tap 251b are discharged together, from And it is separated from interflow refrigerant.
Interflow refrigerant after having separated refrigerating machine oil is discharged from the outlet 11a of shell 10.On the other hand, from combined system The refrigerating machine oil of cryogen separation accumulates the lower side to the inner space of shell 10.Lodge in the lower section of the inner space of shell 10 The refrigerating machine oil of side is flowed into the first oily access 225a, the second oil via the first way to cycle oil 11b, the second way to cycle oil 12b Access 225b.It is supplied to axis 24, each sliding part of the first rotor 22a, the second rotor 22b and each side plate 25a-25c as a result, Position.
As described above, in refrigerating circulatory device, refrigerant (stream can be sucked in the compressor 1 of present embodiment Body), refrigerant is compressed, is then discharged out.In addition, being configured in the compressor 1 of present embodiment in the inner circumferential side of motor part 30 There is compression mechanical part 20, therefore can be realized the whole miniaturization of compressor 1.
In addition, having the first rotor 22a (the first compression mechanical part 20a) and in the compressor 1 of present embodiment Two rotor 22b (the second compression mechanical part 20b), therefore it is capable of forming the first discharge chambe Va and the second discharge chambe Vb.Therefore, root According to applied system (being refrigerating circulatory device in present embodiment), it can easily expand the pressure of the first discharge chambe Va and second Total discharge capacity of contracting room Vb.
At this point, the first rotor 22a and the second rotor 22b are arranged on the central axis direction of cylinder 21, therefore, no Understand to make total enlarged outside diameter for protruding capacity expansion and making cylinder 21.So will not make the stator 31 of motor part 30 with And accommodate the enlarged outside diameter of the main casing 11 of the stator 31.
As a result, compressor 1 according to the present embodiment, can not lead to radial enlargement, and make discharge chambe The capacity expansion of (Va, Vb).
In addition, in the compressor 1 of present embodiment, the eccentric shaft C2 of the first rotor 22a and the second rotor 22b's is inclined Mandrel C2 is configured on coaxial, therefore need not form the position with different eccentric axis in axis 24, is able to easily form axis 24。
In addition, the maximum volume of the first discharge chambe Va and the second discharge chambe Vb are mutual in the compressor 1 of present embodiment It is mutually roughly the same, in addition, when the refrigerant pressure in the first discharge chambe Va reaches maximum pressure cylinder 21 rotation angle θ and second The rotation angle θ of cylinder 21 differs 180 ° when refrigerant pressure in discharge chambe Vb reaches maximum pressure.
As a result, as shown in fig. 6, be able to suppress because expand discharge chambe capacity caused by cogging increase.Cause This, can effectively inhibit the noise of compressor entirety, the increase of vibration.
Herein, Fig. 6 be compare the compressor 1 of present embodiment total torque change and have and the first compression mechanical part The chart of the cogging of the cylinder revolution type compressor (compressor of single cylinder) of the identical single compression mechanical part of 20a. In addition, total torque changes produced by the pressure oscillation of the refrigerant in the first discharge chambe Va for referring to the first compression mechanical part 20a Cogging and the second compression mechanical part 20b the second discharge chambe Vb in refrigerant pressure oscillation caused by torque become Dynamic additive value.
In addition, the first compression of the compressor 1 of the discharge capacity and present embodiment of the compressor of list cylinder shown in fig. 6 Total discharge capacity of room Va and the second discharge chambe Vb is consistent.In addition, the sucking refrigerant pressure of the compressor of list cylinder shown in fig. 6 Power and discharging refrigerant pressure are respectively set as making with the sucking refrigerant pressure of the compressor 1 of present embodiment and discharge Refrigerant pressure is equivalent.
In addition, forming the first oily access in the first rotor 22a, the second rotor 22b in the compressor 1 of present embodiment 225a, the second oily access 225b, therefore axis 24 can be lubricated, the first rotor 22a, the second rotor 22b and each side plate 25a~ Each sliding position of 25c.As a result, the endurance quality of the entirety of compressor 1 can be made to improve.
Especially since being formed with the first oily access 225a, the second oily access 225b, therefore can be effectively by refrigeration machine Oil imported into the first rotor 22a of the central portion of the central axis direction in cylinder 21, the second rotor 22b and intermediate side plate Sliding position between 25c.
In addition, in the compressor 1 of present embodiment, using structure identical with the so-called anti-locking mechanism of pin hole formula rotation As transmission mechanism, therefore transmission mechanism can be realized in simple structure.In addition, the hole portion of transmission mechanism is embedded with ring portion Part 223a, therefore the wearability of hole portion can be made to improve.In turn, the endurance quality of the entirety of compressor 1 can be made to improve.
In addition, the axial end portion in the first oily access 225a, the second oily access 225b forms the first hole portion 221a, the second hole Portion.Therefore, the space for configuring transmission mechanism can be reduced, can further realize the whole miniaturization of compressor 1.
In addition, in the compressor 1 of present embodiment, by axis side suction passage 24d and the first rotor side suction passage 224a, second rotor side suction passage 224b etc., which are formed, to imported into the first discharge chambe Va, second from the refrigerant of outside sucking The suction passage of discharge chambe Vb.Therefore, a part of suction passage and is formed in the first side plate rotated together with cylinder 21 The situation of 25a, the second side plate 25b etc. are compared, and not will lead to the access structure of suction passage, the complication of sealing structure.
In addition, the first tap 251a, the second tap 251b are formed in the first side plate 25a, the second side plate 25b, therefore, It can be easily implemented such structure: by the first compression mechanical part 20a, the second compression mechanical part 20b in the inside of shell 10 It is connected side by side relative to refrigerant stream.
(second embodiment)
Pair as shown in fig. 7, in the present embodiment, the structure of compression mechanical part 20 is changed relative to first embodiment Example be illustrated.Also, Fig. 7 corresponds to the cross-sectional view of the Fig. 3 illustrated in first embodiment, and indicates the first compression The axially vertical section of mechanism 20a.In addition, in Fig. 7, it is identical to part mark identical with first embodiment or equivalent Symbol.This is also in the following embodiments such in illustrated Fig. 8.
More specifically, in the first compression mechanical part 20a of present embodiment, in the periphery side of the first blade 23a Portion is formed with the first articulated section 231a.First articulated section 231a is supported to that the hinged of the inner peripheral surface of cylinder 21 can be formed in It is swung in the circumferential freely with groove portion.Therefore, blade 23 will not leave from cylinder 21, and the inner circumferential side of the first blade 23a is first Slide displacement in groove portion 222a.
In addition, in the inner peripheral side end portion of the first blade 23a, it is formed with and equivalent straight of the width dimensions of the first groove portion 222a The circular-arc part of diameter.When the first blade 23a is swung along with the rotation of cylinder 21 as a result, make the inner circumferential side of the first blade 23a Contact between end and the inner wall of the first groove portion 222a improves, that is, makes the inner peripheral side end portion and first of the first blade 23a Leakproofness between the inner wall of groove portion 222a improves.
The basic structure of second compression mechanical part 20b is as the first compression mechanical part 20a.Therefore, such as the dotted line institute of Fig. 7 Show, the periphery side end of the second blade 23b is also rotatably supported on cylinder.
Other structures and operation are as first embodiment.Therefore, when transporting the compressor 1 of present embodiment Row, then equally run with first embodiment, in refrigerating circulatory device, can suck refrigerant (fluid), and compression is side by side Refrigerant out.In addition, as first embodiment, it is radial big without causing that the capacity of discharge chambe (Va, Vb) can be expanded Type, and inhibit the increase of the noise of compressor entirety, vibration.
(third embodiment)
In the present embodiment, to the structure for changing compression mechanical part 20 relative to second embodiment as shown in Figure 8 Example be illustrated.More specifically, in the first compression mechanical part 20a of present embodiment, by the phase of the first blade 23a Tabular is formed as the inner circumferential side for being located at inner circumferential the first articulated section 231a.
In addition, the first crawler shoe 232a is configured at the inside of the first groove portion 222a in a manner of clamping the first blade 23a, first The cross sectional shape when end on observation of the slave central axis C1 of crawler shoe 232a are as follows: circular a part is cut into rear obtained shape (substantially semi-circular).The axial length of first crawler shoe 232a and the first rotor 22a and the first blade 23a are roughly equal.Second The basic structure of compression mechanical part 20b is as the first compression mechanical part 20a.
Other structures and operation are as second embodiment.Therefore, when transporting the compressor 1 of present embodiment Row, then equally run with second embodiment, in refrigerating circulatory device, can suck refrigerant (fluid), and compression is side by side Refrigerant out.In addition, as first embodiment, it is radial big without causing that the capacity of discharge chambe (Va, Vb) can be expanded Type, and inhibit the increase of the noise of compressor entirety, vibration.
In addition, being configured with crawler shoe 232a in the compressor 1 of present embodiment, therefore the first blade can be effectively improved 23a, the second blade 23b and the first groove portion 222a, the second groove portion 222b inner wall between leakproofness.Thereby, it is possible to improve The compression efficiency of compressor 1.
(other embodiments)
The present invention is not limited to above embodiment, without departing from the spirit and scope of the invention, be able to carry out with Under various deformations.
In the above-described embodiment, to the refrigeration cycle that cylinder revolution type compressor 1 is applied to air conditioner for vehicles Example be illustrated, but cylinder revolution type compressor 1 application it's not limited to that.That is, the rotary-type pressure of cylinder Contracting machine 1 can be applied to extensive purposes as the compressor for compressing various fluids.
In the above-described embodiment, to the component using the structure as the anti-locking mechanism of pin hole formula rotation as cylinder The example of the power transfer unit of revolution type compressor 1 is illustrated, but it's not limited to that for power transfer unit.For example, It can also be using the component of the structure as the anti-locking mechanism of the rotation of cross ring type.
In the above-described embodiment, to the periphery for being configured in the cylinder 21 being integrally formed with rotor using stator The example of the motor part 30 of side is illustrated, but it's not limited to that for motor part 30.For example, it is also possible to by motor part It is arranged with cylinder 21 on the direction central axis C1 of cylinder 21, so that motor part and cylinder 21 be made to link.In addition, can also The central axis C1 of the rotation center of motor part and cylinder 21 not to be configured on coaxial, but via transmission belt by motor The rotary driving force in portion is transmitted to cylinder 21.

Claims (9)

1. a kind of cylinder revolution type compressor, which is characterized in that have:
Around the cylindric cylinder (21) of central axis (C1) rotation；
Cylindric the first rotor (22a) and the second rotor (22b), the first rotor and second rotor configuration are in the cylinder (21) inside, and rotated around the eccentric shaft (C2) of central axis (C1) bias relative to the cylinder (21)；
The first rotor (22a) and second rotor (22b) bearing are that can rotate by axis (24), the axis；
First blade (23a), which is embedded into a manner of it can slide is formed in the of the first rotor (22a) One groove portion (222a), and separate the first discharge chambe (Va), which is formed in the outer peripheral surface of the first rotor (22a) Between the inner peripheral surface of the cylinder (21)；And
Second blade (23b), which is embedded into a manner of it can slide is formed in the of second rotor (22b) Two groove portions (222b), and separate the second discharge chambe (Vb), which is formed in the outer peripheral surface of second rotor (22b) Between the inner peripheral surface of the cylinder (21),
The first rotor (22a) and second rotor (22b) are configured to the central axis (C1) in the cylinder (21) It is arranged on direction,
It is formed with axis side suction passage (24d) in the inside of the axis (24), the axis side suction passage (24d) will inhale from outside The compressed object fluid entered is oriented to first discharge chambe (Va) and second discharge chambe (Vb),
It is formed with first axle side outlet hole (240a) and the second axis side outlet hole (240b) in the outer peripheral surface of the axis (24), it is described First axle side outlet hole makes the compressed object fluid to circulate in the axis side suction passage (24d) to first discharge chambe (Va) Outflow, the second axis side outlet hole make the compressed object fluid to circulate in the axis side suction passage (24d) to described second Discharge chambe (Vb) outflow,
First discharge chambe (Va) and second discharge chambe (Vb) relative to the flowing of the compressed object fluid and it is arranged side by side Ground connection.
2. cylinder revolution type compressor as described in claim 1, which is characterized in that
The eccentric shaft of the first rotor (22a) and the eccentric shaft of second rotor (22b) coaxially configure.
3. cylinder revolution type compressor as claimed in claim 1 or 2, which is characterized in that
The rotation angle (θ) of the cylinder (21) when Fluid pressure in first discharge chambe (Va) reaches maximum pressure and institute The rotation angle (θ) for stating the cylinder (21) when the Fluid pressure in the second discharge chambe (Vb) reaches maximum pressure differs 180 °.
4. cylinder revolution type compressor as claimed in claim 1 or 2, which is characterized in that
The first oily access (225a) and the are respectively formed in the first rotor (22a) and second rotor (22b) Two oily accesses (225b), the first oily access and the second oily access are upwardly extended in the axis of the axis (24), and for cunning The lubricating oil circulation that dynamic position is lubricated.
5. cylinder revolution type compressor as claimed in claim 1 or 2, which is characterized in that have:
Rotary driving force is transmitted to described first turn from the cylinder (21) by transmission mechanism (251c, 221a), the transmission mechanism Sub (22a) and second rotor (22b), so that the first rotor (22a) and second rotor (22b) and the cylinder (21) synchronous rotary；And
Intermediate side plate (25c), the intermediate side plate are configured between the first rotor (22a) and second rotor (22b), point First discharge chambe (Va) and second discharge chambe (Vb) are separated, and is rotated together with the cylinder (21),
The transmission mechanism includes drive pin (251c), and the drive pin is from intermediate side plate (25c) the Xiang Suoshu the first rotor The side (22a) and the side second rotor (22b) are prominent on central axis direction；And first hole portion (221a) and the second hole portion, First hole portion and second hole portion are respectively formed in the first rotor (22a) and second rotor (22b), and described Drive pin (251c) is embedded in first hole portion and second hole portion.
6. cylinder revolution type compressor as claimed in claim 5, which is characterized in that
It is embedded with ring component in first hole portion, second hole portion, the ring component is for inhibiting and the drive pin The abrasion of the inner circumferential side wall surface of (251c) contact.
7. cylinder revolution type compressor as claimed in claim 5, which is characterized in that
It is formed with the first oily access (225a) in the first rotor (22a), the described first oily access (225a) is in the bias The axis of axis (C2) upwardly extends, and the lubricating oil for being lubricated to sliding position circulates,
First hole portion (221a) is formed in the axial end portion of the described first oily access (225a),
It is formed with the second oily access (225b) in second rotor (22b), the described second oily access (225b) is in the bias The axis of axis (C2) upwardly extends, and the lubricating oil for being lubricated to sliding position circulates,
Second hole portion is formed in the axial end portion of the described second oily access (225b).
8. cylinder revolution type compressor as claimed in claim 1 or 2, which is characterized in that have:
Intermediate side plate (25c), the intermediate side plate are configured between the first rotor (22a) and second rotor (22b), point First discharge chambe (Va) and second discharge chambe (Vb) are separated, and is rotated together with the cylinder (21)；
First side plate (25a), first side plate are fixed on the axial one end of the cylinder (21), and with the intermediate side plate (25c) is separated out first discharge chambe (Va) together；And
Second side plate (25b), second side plate are fixed on the axial another side of the cylinder (21), and with the intermediate side plate (25c) is separated out second discharge chambe (Vb) together,
The first rotor side for making compressed object fluid flow into first discharge chambe (Va) is formed in the first rotor (22a) Suction passage (224a),
The first discharge for flowing out compressed object fluid from first discharge chambe (Va) is formed in first side plate (25a) Hole (251a),
The second rotor-side for making compressed object fluid flow into second discharge chambe (Vb) is formed in second rotor (22b) Suction passage (224b),
The second discharge for flowing out compressed object fluid from second discharge chambe (Vb) is formed in second side plate (25b) Hole (251b).
9. cylinder revolution type compressor as claimed in claim 1 or 2, which is characterized in that
Have the motor part (30) for rotating the cylinder (21),
The rotor of the cylinder (21) and the motor part (30) is integrally formed,
The stator arrangement of the motor part (30) is in the peripheral side of the cylinder (21).
CN201680018336.8A 2015-03-27 2016-02-18 Cylinder revolution type compressor Expired - Fee Related CN107532597B (en)

Applications Claiming Priority (3)

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JP2015066056A JP2016186235A (en) 2015-03-27 2015-03-27 Cylinder rotation type compressor
JP2015-066056 2015-03-27
PCT/JP2016/000851 WO2016157688A1 (en) 2015-03-27 2016-02-18 Rotating cylinder type compressor

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JP2016186235A (en) 2016-10-27
DE112016001440T5 (en) 2017-12-14
US20180038372A1 (en) 2018-02-08
KR20170098265A (en) 2017-08-29
CN107532597A (en) 2018-01-02
WO2016157688A1 (en) 2016-10-06

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