CN107110158B - gas compressor - Google Patents

gas compressor Download PDF

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Publication number
CN107110158B
CN107110158B CN201580070926.0A CN201580070926A CN107110158B CN 107110158 B CN107110158 B CN 107110158B CN 201580070926 A CN201580070926 A CN 201580070926A CN 107110158 B CN107110158 B CN 107110158B
Authority
CN
China
Prior art keywords
blade
supply unit
back pressure
rotation
pressure space
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
CN201580070926.0A
Other languages
Chinese (zh)
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CN107110158A (en
Inventor
津田昌宏
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Marelli Corp
Original Assignee
Calsonic Kansei Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2014260492A external-priority patent/JP5878971B1/en
Priority claimed from JP2014260500A external-priority patent/JP5831619B1/en
Priority claimed from JP2014260491A external-priority patent/JP5878970B1/en
Application filed by Calsonic Kansei Corp filed Critical Calsonic Kansei Corp
Publication of CN107110158A publication Critical patent/CN107110158A/en
Application granted granted Critical
Publication of CN107110158B publication Critical patent/CN107110158B/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F04C18/348—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 vanes positively engaging, with circumferential play, an outer rotatable 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
    • 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
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • 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
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids

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

Abstract

It has terminated and has been connected to the 1st supply unit (69a) with the back pressure space (77) of the blade groove (75) of the connection of intermediate pressure feed trough (67) and supplies high pressure from the 1st supply unit (69a), until the refrigerant pressure of the discharge chambe (33a, 33b, 33c) separated by the blade (25) of the blade groove (75) reaches maximal pressure.At the time point for being connected to the 1st supply unit (69a) of high voltage supply slot (69) with the back pressure space (77) of the connection of intermediate pressure feed trough (67) that terminated, the connection of leading back pressure space (77) termination and 1st supply unit (69a) adjacent with the downstream side on the direction of rotation X in the back pressure space (77).

Description

Gas compressor
Technical field
The present invention relates to the gas compressors of so-called blade rotary.
Background technique
As shown in Patent Document 1, previous motion has various gas compressors.
Figure 16 indicates the compression body for being configured at the inside of gas compressor associated with patent document 1.
The compression body has cylinder body 100 and is configured at a pair of of lateral body 101 of the left and right of cylinder body 100.In cylinder body 100 and a pair The inside of lateral body 101 is formed with cylinder chamber 105.Suction inlet 110 and two ejiction openings 108 are equipped in cylinder body 100.
Rotor 102 is rotatably freely configured in cylinder chamber 105.It is formed with multiple blade grooves spaced apartly in rotor 102 106.Blade 103 is configured at each blade groove 106 in such a way that the outer peripheral surface relative to rotor 102 protrude/submerges freely.In blade The part of the 103 backrest surface side of ratio blade of slot 106 is formed with back pressure space 107 (107A, 107B, 107C).Back pressure space 107 exists The two sides of rotor 102 are open.
It is bounded on each side the wall surface by 105 side of cylinder chamber of body 101, is formed with intermediate pressure on the rotational trajectory in back pressure space 107 Feed trough 113 and high voltage supply slot 114.Intermediate pressure is supplied to intermediate pressure feed trough 113, which is the refrigerant than sucking The pressure that pressure is high and the pressure of refrigerant than ejection is low.High pressure is supplied to high voltage supply slot 114, which is and spray The same pressure of the pressure of refrigerant out.
In cylinder chamber 105, discharge chambe 105a, 105b, 105c are formed with by two blades 103 with surrounding.It is rotated in rotor 102 When, discharge chambe 105a, 105b, 105c carry out inhalation process, compression section and spray process, and it is a series of to repeat this Process.
In inhalation process, the volume of discharge chambe 105a, 105b, 105c are become larger, and are sucked and are freezed from suction inlet 110 Agent.In compression section, the volume of discharge chambe 105a, 105b, 105c are gradually become smaller, and compress refrigerant.In spraying process, when The volume of discharge chambe 105a, 105b, 105c gradually become smaller and refrigerant press to regulation pressure it is above when, beat open and close valve 109 It opens and sprays refrigerant from ejiction opening 108.
In such a series of process, the refrigerant pressure of discharge chambe 105a, 105b, 105c is by each blade 103 Each blade 103 is pressed on the direction (hereinafter referred to as " storage direction ") stored to blade groove 106, but is acting on back pressure space Under the action of 107 back pressure, the top of each blade 103 is slided in the inner wall of cylinder chamber 105, so as to make discharge chambe 105a, 105b, 105c reliably compress refrigerant.
Here, upwarding pressure the initial stage of lesser inhalation process, compression section in storage side, will be supplied from intermediate pressure The intermediate pressure of slot 113 makes it play a role as back pressure.In addition, the pressure in the storage direction towards blade 103 is biggish The later period of compression section sprays in process, so that it is played a role as back pressure the high pressure from high voltage supply slot 114.Picture In this way, by changing the back pressure for acting on blade 103 and the pressure in the storage direction towards blade 103 correspondingly, thus Strongly reduce the resistance to sliding of blade 103 and seeks low fuel consumption.
Existing technical literature
Patent document
Patent document 1: Japanese Unexamined Patent Publication 2013-194549 bulletin
Summary of the invention
Problems to be solved by the invention
Figure 17 is to indicate the pressure P105a of discharge chambe 105a, the pressure P105b of discharge chambe 105b and back pressure space 107A Pressure P107A, the chart of corresponding with the rotation angle of rotor variation.It as shown in Figure 17, is 180 degree in angle When, terminate to be connected to the back pressure space 107A of the connection of intermediate pressure feed trough 113 with high voltage supply slot 114.
In the example shown in Figure 16, in back pressure space 107B from the state that is connected to intermediate pressure feed trough 113 to height When the state transformation for pressing feed trough 114 to be connected to, the back pressure space 107A in leading rotation downstream connects with high voltage supply slot 114 It is logical.Therefore, when chase after from the back pressure space 107B of rotation upstream complete to change to the state that is connected to high voltage supply slot 114 when, Two back pressure space 107A, 107B become the state being connected to high voltage supply slot 114 simultaneously.
Since the pressure P107B of the back pressure space 107B of rotation upstream is intermediate pressure, as shown in the P of Figure 17, via The pressure P107A of the back pressure space 107A in the rotation downstream that high voltage supply slot 114 is connected to the back pressure space 107B of rotation upstream Pressure of the meeting temporarily than supplying to high voltage supply slot 114 is low.Later period of compression section, the discharge chambe 105a for spraying process, Therefore the blade 103 that the pressure of the refrigerant of 105b, 105c acts on rotation downstream side on the storage direction of blade 103 is deposited Blade 103 is set temporarily to be accommodated in a possibility that blade groove 106 generates so as to cause vibration.
The present invention is made into view of the situation, it is an object of the present invention to for example, can prevent due to compressing work The generation of the vibration of blade caused by the later period of sequence, the temporary decompression in the back pressure space of the blade of ejection process, also, It is able to maintain that the action performance as gas compressor.
The solution to the problem
In order to achieve the above objectives, gas compressor of the invention has:
The cylinder body of tubular, it is internal that there is the cylinder chamber that can compress refrigerant；
Lateral body is installed on the side of the cylinder body, seals the opening of the cylinder chamber of the side；
Rotor rotates in the cylinder chamber, which has multiple blade grooves in a rotational direction spaced apartly, should With the inner peripheral surface of the cylinder chamber opposite outer peripheral surface opening of multiple blade grooves in the rotor；
Multiple blades, multiple blade are accommodated in each blade groove respectively and protrude/submerge relative to the outer peripheral surface, Multiple blade is slidingly contacted at the inner peripheral surface of the cylinder chamber, and will be separated between the inner peripheral surface and the outer peripheral surface of the rotor Multiple discharge chambes；
Intermediate pressure supply unit is formed at least one of described lateral body, be connected to receiving will from inhalation process to The back pressure space of the slot bottom of the blade groove for the blade that the discharge chambe of compression section separates, and will be than sucking work certainly The big intermediate pressure of refrigerant pressure of the discharge chambe of sequence to compression section is supplied to the back pressure space；And
High voltage supply portion is formed at least one of described lateral body, the back pressure space terminated with it is described in Between press supply unit connection after, the high voltage supply portion be connected to receiving will from compression section to ejection process the discharge chambe The back pressure space of the blade groove of the blade separated, and will be than from compression section to the compression for spraying process The refrigerant pressure of room and the big high voltage supply of the intermediate pressure to the back pressure space,
The high voltage supply portion is divided into multiple supply units independent of each other on the direction of rotation,
The 2nd supply unit from the most upstream side of the direction of rotation positioned at second is formed as following shape: in a leaf In a period of the back pressure space of film trap is connected to the 2nd supply unit, the 2nd supply unit will not be connected to simultaneously in the rotation Turn the back pressure space of upstream side other blade grooves adjacent with the blade groove in direction, and the high voltage supply portion Be formed as the back pressure space for being connected to the blade groove simultaneously and upstream side and the blade groove in the direction of rotation The range in the back pressure space of other adjacent blade grooves.
Detailed description of the invention
Fig. 1 is the integrally-built section view for indicating the gas compressor of rotating vanes of the 1st embodiment of the invention Figure.
Fig. 2 is the cross-sectional view of the I-I line of the gas compressor of Fig. 1.
Fig. 3 is the cross-sectional view of the II-II line of the gas compressor of Fig. 1.
Fig. 4 is the explanatory diagram for enlargedly indicating the major part of compression body shown in Fig. 3.
Fig. 5 is to indicate the 1st supply unit of the high voltage supply slot of Fig. 3 and the 2nd supply unit with the back pressure space of blade groove not The explanatory diagram for imaginary example the case where configuration with being spaced apart that can be connected to any one of the 1st supply unit and the 2nd supply unit.
Fig. 6 is the pressure in the back pressure space of the pressure for indicating the discharge chambe of Fig. 5 and the blade of blade groove and the rotation of rotor The chart of the corresponding variation of gyration.
Fig. 7 be indicate the 1st supply unit and the 2nd supply unit and blade groove of the high voltage supply slot of Fig. 3 back pressure space it Between connection sectional area explanatory diagram.
Fig. 8 is the pressure in the back pressure space of the pressure for indicating the discharge chambe of Fig. 3 and the blade of blade groove and the rotation of rotor The chart of the corresponding variation of gyration.
Fig. 9 is the gas compressor of the rotating vanes of the 2nd embodiment of the invention, opposite with the cross-sectional view of Fig. 2 The cross-sectional view at position answered.
Figure 10 is the gas compressor of the rotating vanes of the 2nd embodiment of the invention, opposite with the cross-sectional view of Fig. 3 The cross-sectional view at position answered.
Figure 11 is the explanatory diagram for enlargedly indicating the major part of compression body shown in Fig. 10.
Figure 12 is indicated in compression body shown in Fig. 10, and the protrusion stroke relative to blade groove of blade is with more than certain Ratio reduction region and the 1st supply unit and the 2nd supply unit between interval between positional relationship explanatory diagram.
Figure 13 is the pressure and rotor in the back pressure space of the pressure for indicating the discharge chambe of Figure 12 and the blade of blade groove Rotate the chart of the corresponding variation of angle.
Figure 14 is indicated in compression body shown in Fig. 10, and the protrusion stroke relative to blade groove of blade is with more than certain Ratio reduction region during having blade sliding contact in, the interval in the region and the 1st supply unit and the 2nd supply unit Between positional relationship explanatory diagram.
Figure 15 is the pressure and rotor in the back pressure space of the pressure for indicating the discharge chambe of Figure 10 and the blade of blade groove Rotate the chart of the corresponding variation of angle.
Figure 16 is the explanatory diagram for indicating the inside of compression body of previous gas compressor.
Figure 17 is the pressure and rotor in the back pressure space of the pressure for indicating the discharge chambe of Figure 16 and the blade of blade groove Rotate the chart of the corresponding variation of angle.
Specific embodiment
[the 1st embodiment]
Referring to Fig.1~Fig. 8 illustrates the 1st embodiment of the invention.
As shown in Figure 1, the gas compressor 1 of present embodiment includes substantially cylindric shell 2, is contained in shell 2 Compression unit 3, to compression unit 3 transmit the motor part 4 of driving force and be fixed on shell 2 and for controlling the driving of motor part 4 Inverter 5.
Shell 2 includes the rear shell for being formed with the front cover 7 of suction inlet (not shown) and the bottomed tube blocked by front cover 7 that is open 9。
Compression unit 3 is fixed in the inner wall 13 of rear shell 9.In compression unit 3, to divide the mode in shell 2 in side shape At there is suction chamber 11, discharge chamber 15 is formed in the other side.Also, it is formed with ejiction opening (not shown) in the periphery of rear shell 9, it should Discharge chamber 15 is connected to by ejiction opening with refrigeration cycle.In addition, being formed with the oily reservoir of oil in reserve O in the lower section of discharge chamber 15 17, oil O are used to keep the lubricity of compression unit 3.
Compression unit 3 includes the compression body 19 to form cylinder chamber 33, the oil eliminator 21 for being fixed on compression body 19, rotates freely Rotor 23 that ground is contained in cylinder chamber 33, the blade 25 for protrude/being submerged relative to rotor 23 and separating cylinder chamber 33 (referring to Fig. 3) with And the drive shaft 27 of driving force is integrally fixed and transmitted with rotor 23.
Compression body 19 includes: the cylinder chamber 33 of cylinder body 29, a pair of of lateral body 31 and the inner circumferential for being formed in cylinder body 29.
As shown in figure 3, cylinder body 29 has the cylinder chamber 33 of the oval shape internally deformed.By being pressed from both sides using a pair of of lateral body 31 The both ends of cylinder body 29 are held, to block the opening of the cylinder chamber 33.
As shown in Figure 3, Figure 4, rotor 23 configures in such a way that its 1 location contacts is in the inner wall of cylinder chamber 33, will be from cylinder chamber The position that 33 center (center of gravity) is deviateed is configured as rotation center, and rotor 23 is open with the outer peripheral surface in rotor 23 The back pressure space 77 of blade groove 75 and the back side positioned at blade 25.
Rotation of the multiple blades 25 that cylinder chamber 33 protrude/is submerged by multiple blade grooves 75 relative to rotor 23 along rotor 23 Direction X is separated into multiple.Multiple compressions are formed between the inner peripheral surface 33d of cylinder chamber 33 and the outer peripheral surface 23a of rotor 23 as a result, Room 33a, 33b, 33c.
Moreover, cylinder body 29 includes inlet hole 39, refrigerant is sucked into cylinder chamber 33；Squit hole 35, will be in cylinder chamber Compressed refrigerant sprays in 33；Open and close valve 37 is used to be opened and closed squit hole 35；And cylinder side oil feed path 41, with The oily feed path of lateral body 31 is connected to.
As shown in Figure 1, a pair of of lateral body 31 includes front side body 31a and rear side body 31b, oily separation is fixed in rear side body 31b Device 21.
Front side body 31a includes front end face 43, abuts with cylinder body 29；Inlet hole (not shown) connects with inlet hole 39 It is logical, and refrigerant is sucked from suction chamber 11；Front side bearing 47, drive shaft 27 is rotatably supported；And front side oil supplies To path 49, it is connected to cylinder side oil feed path 41.
It is equipped with pressure feed trough in front end face 43, pressure feed trough includes intermediate pressure feed trough 51, to back pressure space 77 supply the pressure (intermediate pressure) of the low centre of higher than the pressure of the refrigerant of sucking and the refrigerant than spraying pressure；With And high voltage supply slot 53, it is set to the position opposite with the high voltage supply slot 69 of the side rear side body 31b.
Moreover, being formed with cricoid front side endless groove 55 in front side bearing 47, front side endless groove 55 and front side oil supply road The one end of diameter 49 is communicatively arranged.In addition, the another side of front side oil feed path 49 is connected to cylinder side oil feed path 41.
As shown in Fig. 2, rear side body 31b includes back end surface 57, abutted with cylinder body 29；Oily supply hole 59, will storage Oily O in the lower section of discharge chamber 15 is sucked；Rear side bearing 63, drive shaft 27 is rotatably supported；And rear side oil supplies Path 59b is given, is connected to cylinder side oil feed path 41.
Back end surface 57 includes squit hole 61, is used to spray refrigerant compressed in cylinder chamber 33；Intermediate pressure supplies Slot 67 (being equivalent to the intermediate pressure supply unit in claim) is given, the pressure to the supply of back pressure space 77 than the refrigerant of sucking The oil of the low intermediate pressure of (sucking pressure) high and the refrigerant than spraying pressure (spraying pressure)；And high voltage supply slot 69 is (quite High voltage supply portion in claim), the pressure (spraying pressure) as the refrigerant sprayed is supplied to back pressure space 77 The oil of high pressure.
High voltage supply slot 69 is divided into the 1st supply unit 69a independent of each other (quite on the direction of rotation X of rotor 23 Supply unit in upstream side) and the 2nd supply unit 69b (supply unit for being equivalent to downstream side).
Moreover, being open respectively in the 1st supply unit 69a and the 2nd supply unit 69b has high voltage supply access 71a, 71b, each height Pressure supply passageway 71a, 71b one end be connected to rear side endless groove 73, another side be respectively communicated in the 1st supply unit 69a with And the 2nd supply unit 69b.
In addition, the high voltage supply slot 53 opposite with high voltage supply slot 69 of front side body 31a is also divided into and the 1st supply unit Same two supply units (not shown) of 69a and the 2nd supply unit 69b.
For being formed in the back pressure space 77 (referring to Fig. 3, Fig. 4) of rotor 23, by rotating rotor 23, before compression Half fragment position, back pressure space 77 are connected to intermediate pressure feed trough 51,67, in the later half fragment position of compression, back pressure space 77 and height Feed trough 53,69 is pressed to be connected to.
In the state shown in fig. 4, the discharge chambe of compression section will be moved to from inhalation process by the rotation of rotor 23 The downstream side of 33b and the discharge chambe 33b on the direction of rotation X of rotor 23 are simultaneously moved to the pressure for spraying process from compression section The connection of back pressure space the 77B termination and intermediate pressure feed trough 67 of the blade groove 75 for the blade 25B that contracting room 33a separates.Also, it carries on the back Pressure space 77B is connected to the 1st supply unit 69a of the upstream side on the direction of rotation X for being located at rotor 23 since then.
In this state, the blade of the leading blade 25A in the downstream side of the blade 25B on the direction of rotation X of rotor 23 The connection that the back pressure space 77A of slot 75 has terminated with the 1st supply unit 69a, the with the downstream side being located on the X of direction of rotation the 2nd Supply unit 69b connection.
Then, the 1st supply unit 69a is formed as following shape: on the direction of rotation X of rotor 23, leading blade 25A's Back pressure space 77A and chase after from the back pressure space 77B of the next blade 25B in blade 25A will not be connected to simultaneously the 1st supply Portion 69a.That is, the 1st supply unit 69a is formed are as follows: on the direction of rotation X of rotor 23, the angle model of the extension of the 1st supply unit 69a The difference for enclosing the angle being located at than the back pressure space 77A angle being located at and back pressure space 77B is small.That is, rotor 23 The distance between back pressure space 77A and back pressure space 77B on the X of direction of rotation are set to the width than the 1st supply unit 69a It is wide.
Similarly, the 2nd supply unit 69b is formed as following shape: on the direction of rotation X of rotor 23, leading blade 25A Back pressure space 77A and chase after from the back pressure space 77B of the next blade 25B in blade 25A will not be connected to simultaneously the 2nd confession Give portion 69b.That is, the 2nd supply unit 69b is formed are as follows: on the direction of rotation X of rotor 23, the angle of the extension of the 2nd supply unit 69b Range is smaller than the difference for the angle that the back pressure space 77A angle being located at and back pressure space 77B are located at.That is, rotor 23 Direction of rotation X on back pressure space 77A and the distance between back pressure space 77B be set to the width than the 2nd supply unit 69b It is wide.
As described above, the difference for the angle being located at according to the back pressure space 77A angle being located at and back pressure space 77B, The angle for generating the limitation relative to the 1st supply unit 69a angular range extended and being extended relative to the 2nd supply unit 69b Spend the limitation of range.
Similarly, the difference for the angle being located at according to the back pressure space 77B angle being located at and back pressure space 77C generates Limitation relative to the 1st supply unit 69a angular range extended and the angle model that is extended relative to the 2nd supply unit 69b The limitation enclosed.
Similarly, the difference for the angle being located at according to the back pressure space 77C angle being located at and back pressure space 77A generates Limitation relative to the 1st supply unit 69a angular range extended and the angle model that is extended relative to the 2nd supply unit 69b The limitation enclosed.
Like this, according to the angle that back pressure space 77 is located on the direction of rotation X of rotor 23, to determine the 1st supply The shape of portion 69a and the 2nd supply unit 69b.
In addition, the distance between intermediate pressure feed trough 67 and the 1st supply unit 69a on the direction of rotation X of rotor 23 and The distance between 2nd supply unit 69b and intermediate pressure feed trough 67 are set to the back pressure space on the direction of rotation X than rotor 23 77 width is wide.
As shown in Figure 1, oil supply hole 59 and rear side oil feed path 59a is communicatively formed, from rear side oil feed path 59a Branch it is formed with the oily feed path 59b of rear side.Rear side oil feed path 59b is connected to cylinder side oil feed path 41.
It is formed with cricoid rear side endless groove 73 in rear side bearing 63, rear side endless groove 73 and rear side communication path 65 connect It is logical.The one end of rear side communication path 65 is connected to rear side endless groove 73, and another side is open in high voltage supply slot 69.
Oil eliminator 21 is fixed on rear side body 31b, and compressed refrigerant flows into oil eliminator 21, oil in cylinder chamber 33 Refrigerant is separated with oil O from device 21.
Rotor 23 is fixed in the side of drive shaft 27, and drive shaft 27 is supported by the bearing 47,63 of each lateral body 31a, 31b To rotate freely.Moreover, being fixed with motor part 4 in the other side of drive shaft 27.
Motor part 4 includes stator 79, is fixed on the inner wall 13 of rear shell 9；And motor rotor 81, rotatably freely It is configured at the inner circumferential side of stator 79, is rotated under the magnetic force.By under the magnetic force rotating motor rotor 81, from And rotary driving force is transmitted to compression unit 3.
Here, to the 1st supply unit 69a and the 2nd supply unit 69b of the high voltage supply slot 69 on the direction of rotation X of rotor 23 Between interval be illustrated.
In the present embodiment, as shown in Figure 3, Figure 4, the 1st supply unit 69a on the direction of rotation X of rotor 23 and the 2nd is supplied It is set to the distance between portion 69b narrower than the width in the back pressure space 77 on the direction of rotation X of rotor 23.
Here, as shown in figure 5, the 1st supply unit 69a of the high voltage supply slot 69 on the direction of rotation X of rotor 23 and the 2nd is supplied It is assumed to the interval between portion 69b wider than the width in back pressure space 77.Fig. 5 is to indicate to supply the 1st of the high voltage supply slot of Fig. 3 the Between will not being connected to any one of the 1st supply unit and the 2nd supply unit to portion and the 2nd supply unit with the back pressure space of blade groove Every discretely configure the case where imaginary example explanatory diagram.
Fig. 6 is the pressure for indicating the pressure P33a of discharge chambe 33a, the pressure P33b of discharge chambe 33b and back pressure space 77B The chart of variation corresponding with the rotation angle of rotor.As shown in Figure 6, when angle is 180 degree, finish and centre The back pressure space 77B of the connection of feed trough 67 is pressed to be connected to high voltage supply slot 69.In the present embodiment, high voltage supply slot 69 by 1st supply unit 69a and the 2nd supply unit 69b is constituted, along with the rotation of the rotor 23 rotated along direction of rotation X, back pressure space 77B is connected to the 2nd supply unit 69b after being connected to the 1st supply unit 69a.
Due between the 1st supply unit 69a and the 2nd supply unit 69b of the high voltage supply slot 69 on the direction of rotation X of rotor 23 Interval it is wider than the width of back pressure space 77B, therefore, in back pressure space, the connection target of 77B is changed into from the 1st supply unit 69a When the 2nd supply unit 69b, generates any one of back pressure space 77B and the 1st supply unit 69a and the 2nd supply unit 69b and be not connected to State.
At this point, since discharge chambe 33a, 33b for being separated by blade 25B enter ejection process from the later period of compression section, Therefore, it is contained in the blade 25B of blade groove 75 of the back pressure space 77B between the 1st supply unit 69a and the 2nd supply unit 69b certainly Power of the inner peripheral surface 33d of cylinder chamber 33 by the direction submerged to blade groove 75.That is, being located at the 1st supply unit in back pressure space 77B When between 69a and the 2nd supply unit 69b, the volume of back pressure space 77B is in the situation of reduction.
But, due to descending any one of back pressure space 77B and the 1st supply unit 69a and the 2nd supply unit 69b in the position It is not connected to, therefore, high pressure corresponding with the amount of volume of reduction of back pressure space 77B, which can not keep out of the way, removes back pressure space Any one other than 77B.Therefore, turn in the connection target of back pressure space 77B from the 1st supply unit 69a to the 2nd supply unit 69b In stage in the way of change, as shown in the P1 of Fig. 6, the pressure in back pressure space 77 temporarily rises.That is, due to generating back pressure space The all disconnected state of any one of 77B and the 1st supply unit 69a and the 2nd supply unit 69b, therefore, as shown in the P1 of Fig. 6, back The pressure in pressure space 77 temporarily rises.
When the pressure for generating such back pressure space 77B rises, from the inner peripheral surface 33d of cylinder chamber 33 by blade groove 75 The blade 25B of the power in the direction submerged is intended to prominent from blade groove 75 under the action of the pressure of the back pressure space 77B of rising.This If sample, the pressing force of inner peripheral surface 33d there are blade 25B, relative to cylinder chamber 33 excessively increases, blade 25B and cylinder chamber 33 Inner peripheral surface 33d between resistance to sliding increase a possibility that.
Same phenomenon also can be in any one of blade 25A, blade 25C and the 1st supply unit 69a and the 2nd supply unit 69b It is generated under all disconnected state.
Here, in the gas compressor 1 of present embodiment, as shown in fig. 7, back pressure space 77 connection target from When 1 supply unit 69a changes to the 2nd supply unit 69b, by between back pressure space 77 and the 1st supply unit 69a connection sectional area S1 and Sectional area obtained by connection sectional area S3 between back pressure space 77 and the 2nd supply unit 69b is amounted to ensures more than centainly.
Specifically, back pressure space can be made when back pressure space 77 is connected to the 1st supply unit 69a, the 2nd supply unit 69b 77 high pressure is kept out of the way to lower portion, that is, to the high voltage supply of the oily O of the 1st supply unit 69a, the 2nd supply unit 69b supply high pressure Access 71a, 71b, the rear side communication path 65 for being connected to high voltage supply access 71a, 71b, rear side endless groove 73, the supply of rear side oil Path 59a and oily supply hole 59.
In order to ensure keeping out of the way path with the same above high pressure in above-mentioned path, in the gas compressor 1 of present embodiment, On the direction of rotation X of rotor 23, make that there is interval as following between the 1st supply unit 69a and the 2nd supply unit 69b, between being somebody's turn to do Every making adding up to for above-mentioned connection sectional area S1, S3, from high voltage supply access 71a, 71b to oily supply hole 59, high pressure Oily O the feed path relative to the 1st supply unit 69a, the 2nd supply unit 69b minimum path sectional area more than.
Then, the movement of the gas compressor of present embodiment 1 is illustrated.
Firstly, under the control of inverter 5 shown in Fig. 1, coil stream of the electric current to the stator 79 for being wound in motor part 4 It is dynamic.By making electric current to coil flowing to generate magnetic force, the motor rotor 81 for the inner circumferential configured in stator 79 rotates.
It is rotated by motor rotor 81, the drive shaft 27 that side is fixed with motor rotor 81 at one end rotates, to be fixed on The rotor 23 of the another side of drive shaft 27 also rotates.
Along with the rotation of rotor 23, refrigerant flows into suction chamber 11, and refrigerant is from suction chamber 11 via front side body 31a's Inlet hole (not shown) sucks (inhalation process) to cylinder chamber 33.For the refrigerant sucked to cylinder chamber 33, multiple blades 25 are utilized Discharge chambe 33a, 33b, 33c are formed in cylinder chamber 33, rotate to compress the system in discharge chambe 33a, 33b, 33c by rotor 23 Cryogen (compression section).
Compressed refrigerant pushes open and close valve 37 open and sprays from squit hole 35 and (spray process) in cylinder chamber 33, then self-spray Portal 61 via oil eliminator 21 to discharge chamber 15 spray.In addition, being divided from the refrigerant that squit hole 61 sprays by oil eliminator 21 From at refrigerant and oil O, refrigerant is sprayed from ejiction opening (not shown) to refrigeration cycle (not shown), and oily O is stored in discharge chamber 15 lower section.
The oil for being stored in the lower section of discharge chamber 15 passes through rear side oil feed path 59a from the oily supply hole 59 of rear side body 31b It is supplied by side bearing 63 backward.
It is throttled between drive shaft 27 by the oil for the high pressure that side bearing 63 supplies backward, to become the system than sucking The low intermediate pressure of high and the refrigerant than spraying the pressure (spraying pressure) of pressure (sucking pressure) of cryogen, becomes the oily O of intermediate pressure Pass through the gap between drive shaft 27 and rear side body 31b and is supplied to intermediate pressure feed trough 67.
As shown in figure 3, for the oily O of the intermediate pressure supplied to intermediate pressure feed trough 67, in the sucking work certainly of refrigerant In the range of sequence to compression section, intermediate pressure is supplied to back pressure space 77, makes blade to the back side of blade 25 supply intermediate pressure 25 is prominent from blade groove 75.
Moreover, being opened by the oily O for the high pressure that side bearing 63 supplies backward via the comfortable back end surface 57 of rear side communication path 65 High voltage supply access 71a, 71b of mouth is supplied to the 1st supply unit 69a of high voltage supply slot 69 and the 2nd supply unit 69b.
As shown in figure 3, freezing for the oily O of the high pressure supplied to the 1st supply unit 69a and the 2nd supply unit 69b Agent from compression section to spray process in the range of, to back pressure space 77 supply high pressure, to the back side of blade 25 supply high pressure So that blade 25 is prominent from blade groove 75.Moreover, the 1st supply unit 69a and the 2nd supply unit 69b is via back pressure space 77 with before The high voltage supply slot 53 of the side lateral body 31a, corresponding each supply unit (not shown) is connected, also from each confession of high voltage supply slot 53 High pressure is supplied to back pressure space 77 to portion.
Moreover, the oily O of high pressure flows into the oily feed path 59a of rear side from oily supply hole 59, from rear side oil feed path 59a points Branch is by rear side oil feed path 59b, via cylinder side oil feed path 41 from front side oil feed path 49 by side bearing 47 forward Supply.
The oily O for being fed into the high pressure of front side bearing 47 is throttled between drive shaft 27, thus become intermediate pressure, at It is supplied by the gap between drive shaft 27 and front side body 31a and for the oily O of intermediate pressure to intermediate pressure feed trough 51.
The oily O for the high pressure come from the supply of high voltage supply slot 53,69 of front side body 31a and rear side body 31b is in rotor 23 It rotates later half fragment position to be supplied to the back pressure space 77 of rotor 23, application makes blade 25 from the back pressure outstanding of blade groove 75.
Using the gas compressor 1 of present embodiment, terminate and the blade groove 75 of the connection of intermediate pressure feed trough 67 Back pressure space 77 is connected to the 1st supply unit 69a of high voltage supply slot 69, supplies high pressure from the 1st supply unit 69a.
Later, for the back pressure space 77, in the back of the next blade groove 75 for the upstream side being located on the X of direction of rotation Pressure space 77 is connected to the connection to terminate before the 1st supply unit 69a with the 1st supply unit 69a, independent relative to the 1st supply unit 69a The 2nd supply unit 69b in downstream side being located on the X of direction of rotation can be connected to the back pressure space, it is empty relative to the back pressure again Between supply high pressure.
Therefore, the of high voltage supply slot 69 is connected to the back pressure space 77 of the connection of intermediate pressure feed trough 67 having terminated On the time point of 1 supply unit 69a, the leading back pressure space adjacent with the downstream side on the direction of rotation X in the back pressure space 77 77 will not be connected to the 1st supply unit 69a simultaneously.
Following situation is shown in FIG. 4, for back pressure space 77A, in the following of the upstream side positioned at direction of rotation X The back pressure space 77B of blade groove 75 be connected to the connection to terminate with the 1st supply unit 69a before the 1st supply unit 69a, relative to The 2nd supply unit 69b in the independent downstream side on the X of direction of rotation the 1st supply unit 69a can be connected to back pressure space 77A, High pressure is supplied relative to back pressure space 77A again.
Therefore, on the time point of the 1st supply unit 69a that 77B is connected to high voltage supply slot 69 in back pressure space, with the back pressure The adjacent leading back pressure space 77A in downstream side on the direction of rotation X of space 77B will not connect with the 1st supply unit 69a simultaneously It is logical.For same relationship, not only between back pressure space 77A and back pressure space 77B, in back pressure space 77B and back pressure space It is also set up between 77C, between back pressure space 77C and back pressure space 77A.
By making two back pressure spaces 77 not be connected to the 1st supply unit 69a simultaneously, leading back pressure space 77 can be prevented Pressure because chase after from next back pressure space 77 rise to high pressure before intermediate pressure due to temporarily from high drops. Thereby, it is possible to prevent the temporary decompression in the back pressure space 77 of the blade 25 of the early period of compression section cause blade 25 relative to The generation for such vibration that the inner peripheral surface 33d of cylinder chamber 33 is contacted repeatedly/left.
In addition, for back pressure space 77, in the back pressure of the next blade groove 75 for the upstream side being located on the X of direction of rotation Space 77 is connected to the connection to terminate before the 2nd supply unit 69b with the 2nd supply unit 69b.Therefore, it is terminating and high voltage supply The back pressure space 77 of the connection of 1st supply unit 69a of slot 69 is connected to the time point of the 2nd supply unit 69b of high voltage supply slot 69 On, the leading back pressure space 77 adjacent with the downstream side on the direction of rotation X in the back pressure space 77 will not be supplied with the 2nd simultaneously Portion 69b connection.
Fig. 8 is the pressure for indicating the pressure P33a of discharge chambe 33a, the pressure P33b of discharge chambe 33b and back pressure space 77B The chart of variation corresponding with the rotation angle of rotor.As shown in Figure 8, when angle is 180 degree, finish and centre The back pressure space 77B of the connection of feed trough 67 is pressed to be connected to high voltage supply slot 69.In the present embodiment, high voltage supply slot 69 by 1st supply unit 69a and the 2nd supply unit 69b is constituted, along with the rotation of the rotor 23 rotated along direction of rotation X, back pressure space 77B is connected to the 2nd supply unit 69b after being connected to the 1st supply unit 69a.
As shown in the P in the chart of Figure 17, generate following phenomenon: the pressure in leading back pressure space 107 is due to chasing after From next back pressure space 107 from the pressure in the way that intermediate pressure rises to high pressure and temporarily from high drops. But be connected to when by keeping two back pressure spaces 77 different with the 2nd supply unit 69b, it can prevent as illustrated in the graph of figure 8 Above-mentioned phenomenon.Thereby, it is possible to prevent the temporary of back pressure space 77 in the later period of compression section, the blade 25 for spraying process from subtracting Pressure causes blade 25 relative to the generation of the inner peripheral surface 33d of the cylinder chamber 33 such vibration for contacting/leaving repeatedly.
Also, using the gas compressor 1 of present embodiment, by the connection target in back pressure space 77 from the 1st supply unit 69a Connection sectional area between when changing to the 2nd supply unit 69b, back pressure space 77 and the 1st supply unit 69a, the 2nd supply unit 69b The total of S1, S3 are set as the minimum path of the feed path relative to the 1st supply unit 69a, the 2nd supply unit 69b of the oily O of high pressure It is more than sectional area.
Back pressure space 77 connection target from the stage in the way that the 1st supply unit 69a changes to the 2nd supply unit 69b, back Press space 77 with sectional area and at least one of the 1st supply unit 69a and the 2nd supply unit 69b more than minimum path sectional area Connection, thus, it is possible to ensure the high pressure in back pressure space 77 to keep out of the way target.
Therefore, above structure can be utilized, prevents following phenomenon: the P1 in the chart of Fig. 6 as illustrated in the graph of figure 8 Shown such phenomenon, that is, when the connection target in back pressure space 77 changes from the 1st supply unit 69a to the 2nd supply unit 69b, because The pressure in back pressure space 77 caused by the sectional area deficiency for keeping out of the way path of the high pressure in back pressure space 77 temporarily rises The phenomenon that,.
Thereby, it is possible to prevent due to back pressure space 77 temporary pressure rise cause blade 25 relative to cylinder chamber 33 The pressing force of inner peripheral surface 33d excessively increase, prevent resistance to sliding between the two from increasing.Therefore, compression section can be prevented The temporary pressurization in later period, the back pressure space 77 for spraying process lead to the inner peripheral surface 33d relative to cylinder chamber 33 of blade 25 Resistance to sliding increase and power needed for the rotation of rotor 23 increase, be able to maintain that the action performance as gas compressor 1.
Additionally it may be desirable to which the 2nd supply unit 69b in high voltage supply slot 69 will not be on the direction of rotation X of rotor 23 together When be connected in the range of two adjacent back pressure spaces 77, the 2nd supply unit 69b is set as much as possible on the X of direction of rotation The shape of larger size.By doing so, can make due to the connection with the 1st supply unit 69a and towards high pressure from intermediate pressure The back pressure space 77 of pressure increase is set just to be connected to the 2nd supply from the earlier stage of the compression section of discharge chambe 33a, 33b, 33c Portion 69b stablizes the pressure in back pressure space 77 in high pressure later.
Thereby, it is possible to start the ejection process of discharge chambe 33a, 33b, 33c in earlier stage, squit hole 35 can be made Open and close valve 37 sprays the high-pressure refrigerant in discharge chambe 33a, 33b, 33c efficiently fully in earlier stage valve opening, can Seek to improve refrigerant compression power.
In the present embodiment, high voltage supply slot 69 is divided into two the 1st supplies independent of each other on the X of direction of rotation Portion 69a and the 2nd supply unit 69b.But high voltage supply slot 69 is divided into 3 or more supply units on the X of direction of rotation The present invention can also be applied for situation.In this case, in back pressure space 77 on the X of direction of rotation across two adjacent supply units When mobile, the connection sectional area between the supply unit of upstream side, the supply unit in downstream side and back pressure space 77 can also be fitted With relationship of the invention.
[the 2nd embodiment]
Then, the 2nd embodiment of the invention is illustrated referring to Fig. 9~Figure 15.
Fig. 9, Figure 10 indicate the construction of the gas compressor of the rotating vanes of the 2nd embodiment.2nd embodiment has The rear side body 31b2 different from the rear side body 31b of the 1st embodiment.Structure and the 1st embodiment phase other than rear side body 31b2 Together.For constituting parts identical with the 1st embodiment, identical appended drawing reference is marked in the accompanying drawings and is omitted the description, is only said Bright different structure.
In the present embodiment, on the direction of rotation X of rotor 23, the 1st supply unit 69a and the 2nd supply unit 69b it Between be equipped with blade groove 75 77 or more back pressure space size interval 69c.That is, being set to the supply of the 1st supply unit 69a and the 2nd Interval 69c between portion 69b is set to wider than the width in the back pressure space 77 of blade groove 75.
In the state shown in Figure 11, the discharge chambe of compression section will be moved to from inhalation process by the rotation of rotor 23 The downstream side of 33b and the discharge chambe 33b on the direction of rotation X of rotor 23 are simultaneously moved to the pressure for spraying process from compression section The back pressure space 77B of blade groove 75 for the blade 25B that contracting room 33a separates is connected to the 1st supply unit 69a of high voltage supply slot 69.
In this state, the blade of the leading blade 25A in the downstream side of the blade 25B on the direction of rotation X of rotor 23 The connection that the back pressure space 77A of slot 75 has terminated with the 2nd supply unit 69b starts and is located in the downstream side of direction of rotation X Between pressure supply unit 67 be connected to.
Here, to the 1st supply unit 69a and the 2nd supply unit 69b of the high voltage supply slot 69 on the direction of rotation X of rotor 23 Between the position of interval 69c be illustrated.After state shown in Figure 11, when rotor 23 is rotated towards direction of rotation X, Back pressure space 77B terminates the connection of itself and the 1st supply unit 69a, and back pressure space 77B is supplied with the 1st supply unit 69a and the 2nd is set to Interval 69c connection between portion 69b.Appointing in back pressure space 77B and the 1st supply unit 69a and the 2nd supply unit 69b is generated at this time The disconnected state of one.
In this state, if along with rotor 23 the rotation to direction of rotation X, blade 25B is relative to blade groove 75 Prominent stroke is reduced, then the volume of back pressure space 77B is reduced.At this point, due to back pressure space 77B and the 1st supply unit 69a and the 2nd Any one of supply unit 69b is not connected to, therefore, it is impossible to make high pressure corresponding with the amount of volume reduction to the 1st supply unit 69a, the 2nd supply unit 69b keep out of the way.
Herein it is assumed that such situation, interval 69c configuration is in following position: in the inner peripheral surface of blade 25B and cylinder chamber 33 When region sliding contact shown in the range of (A) of Figure 12 of 33d, that is, blade 25B and the direction rotation side along with rotor 23 To the rotation of X, blade 25B the prominent stroke relative to blade groove 75 with the region sliding contact of more than a certain amount of ratio reduction When, position that back pressure space 77B is connected to.
Figure 12 is to indicate the protrusion stroke relative to blade groove 75 of blade 25B with the region of more than a certain amount of ratio reduction The explanatory diagram of positional relationship between the 69c of interval.
In this case, in the state that back pressure space 77B is blocked from the 1st supply unit 69a and the 2nd supply unit 69b, back Pressure space 77B volume reduced with ratio corresponding with the slip of protrusion stroke of blade 25B, as shown in the P1 of Figure 13 that The pressure of sample, back pressure space 77B temporarily rises.
When the pressure for generating such back pressure space 77B rises, from the inner peripheral surface 33d of cylinder chamber 33 by blade groove 75 The blade 25B of the power in the direction submerged is intended to prominent from blade groove 75 under the action of the pressure of the rising of back pressure space 77B.In this way If, there are the pressing forces of the inner peripheral surface 33d relative to cylinder chamber 33 of blade 25B excessively to increase, blade 25B and cylinder chamber 33 it is interior A possibility that resistance to sliding between circumferential surface 33d increases.
Here, configuration space 69c as follows: by the inner peripheral surface 33d of cylinder chamber 33, along with rotor 23 direction rotation The slip for turning the protrusion stroke relative to blade groove 75 of the blade 25 of the rotation of direction X becomes lower than above-mentioned certain ratio Defined threshold value slip below slip lesser region of the region as prominent stroke, in the gas of present embodiment In gas compressor 1, at the lesser region of slip that blade 25 is slidingly contacted at the protrusion stroke, back pressure space 77 and interval 69c connection.
Specifically, in the present embodiment, as shown in figure 14, the inner peripheral surface 33d of cylinder chamber 33 is formed as following 4 regions It is successively continuous on the direction of rotation X of rotor 23,
(a) with the protrusion stroke from blade groove 75 of the blade 25 of the inner peripheral surface 33d sliding contact of cylinder chamber 33 along with turn Son 23 the rotation towards direction of rotation X and increased region,
(b) with the protrusion stroke from blade groove 75 of the blade 25 of the inner peripheral surface 33d sliding contact of cylinder chamber 33 along with turn Son 23 the rotation towards direction of rotation X and reduction region,
(c) with the protrusion stroke from blade groove 75 of the blade 25 of the inner peripheral surface 33d sliding contact of cylinder chamber 33 along with turn The rotation towards direction of rotation X of son 23 and reduce and region that the slip in the region of its slip ratio (b) is small,
(d) with the protrusion stroke from blade groove 75 of the blade 25 of the inner peripheral surface 33d sliding contact of cylinder chamber 33 along with turn The rotation towards direction of rotation X of son 23 and reduce and the slip in the region of its slip ratio (c) is big and the region than (b) The small region of slip.
Here, 69c configuration will be spaced in following position: being slidingly contacted at the direction rotation along with rotor 23 in blade 25 When the region of the slip of the protrusion stroke of the blade 25 of the rotation of direction X minimum (c), position that back pressure space 77 is connected to It sets.
Next, being illustrated to the movement of the gas compressor 1 of present embodiment.
In the present embodiment, terminated with the back pressure space 77 of the connection of intermediate pressure feed trough 67 be connected to high pressure supply It is adjacent with the downstream side on the direction of rotation X in the back pressure space 77 leading to the time point of the 1st supply unit 69a of slot 69 Back pressure space 77 will not be connected to the 1st supply unit 69a simultaneously.
Therefore, the of high voltage supply slot 69 is connected to the back pressure space 77 of the connection of intermediate pressure feed trough 67 having terminated The time point of 1 supply unit 69a, the leading back pressure space 77 adjacent with the downstream side on the direction of rotation X in the back pressure space 77 It will not be connected to simultaneously with the 1st supply unit 69a.
By making two back pressure spaces 77 not be connected to the 1st supply unit 69a simultaneously, leading back pressure space 77 can be prevented Pressure because chase after from next back pressure space 77 rise to high pressure before intermediate pressure due to temporarily from high drops. Thereby, it is possible to prevent the temporary decompression in the back pressure space 77 of the blade 25 of the early period of compression section cause blade 25 relative to The generation for such vibration that the inner peripheral surface 33d of cylinder chamber 33 is contacted repeatedly/left.
Moreover, back pressure space 77 is in the back pressure space 77 of the next blade groove 75 of the upstream side positioned at direction of rotation X It is connected to the connection to terminate before the 2nd supply unit 69b with the 2nd supply unit 69b.Therefore, it is terminating and high voltage supply slot 69 The back pressure space 77 of the connection of 1st supply unit 69a is connected to the time point of the 2nd supply unit 69b of high voltage supply slot 69, with the back The leading back pressure space 77 for pressing the downstream side on the direction of rotation X in space 77 adjacent will not connect with the 2nd supply unit 69b simultaneously It is logical.
Therefore, as shown in the chart of Figure 15, the later period of compression section, the back pressure for the blade 25 for spraying process can be prevented empty Between 77 temporary decompression such vibration for causing blade 25 to contact/leave repeatedly relative to the inner peripheral surface 33d of cylinder chamber 33 Generation.
Also, using the gas compressor 1 of present embodiment, the supply of the 1st supply unit 69a and the 2nd is set as follows The position of interval 69c between portion 69b, that is, between back pressure space 77 and the 1st supply unit 69a and the 2nd supply unit 69b When 69c connection, the blade 25 of the blade groove for being contained in the back pressure space 77 75 is made to be slidingly contacted at the direction with rotor 23 The region of the slip of the protrusion stroke of the blade 25 of the rotation of direction of rotation X minimum (c).
Therefore, when the interval 69c between back pressure space 77 and the 1st supply unit 69a and the 2nd supply unit 69b is connected to, blade 25 protrusion stroke is hardly reduced as the part that the round frame of Figure 15 is surrounded, and the volume in back pressure space 77 also hardly subtracts It is few.Therefore, as shown in Figure 15, the temporary of back pressure space 77 is not generated when back pressure space 77 is connected to interval 69c Pressure increase.
Therefore, as shown in the P1 in the chart of Figure 13, the connection target in back pressure space 77 is the 1st supply unit 69a And when the 2nd interval 69c between supply unit 69b, the high pressure in back pressure space 77 can be prevented as shown in the chart of Figure 15 Keep out of the way the phenomenon that path disappears, the pressure in back pressure space 77 temporarily rises.
Thereby, it is possible to prevent due to back pressure space 77 temporary pressure rise cause blade 25 relative to cylinder chamber 33 The pressing force of inner peripheral surface 33d excessively increase and resistance to sliding between the two increases.Thus, it is possible to after preventing compression section The temporary pressurization of phase, the back pressure space 77 for spraying process lead to the cunning of the inner peripheral surface 33d relative to cylinder chamber 33 of blade 25 Dynamic resistance increases and power needed for the rotation of rotor 23 increases, and is able to maintain that the action performance as gas compressor 1.
Additionally it may be desirable to which the rotation in rotor 23 will not be connected to simultaneously in the 2nd supply unit 69b of high voltage supply slot 69 In the range of turning two back pressure spaces 77 adjacent on the X of direction, the 2nd supply unit 69b is set as much as possible on the X of direction of rotation The shape of larger size.By doing so, can make due to the connection with the 1st supply unit 69a and towards high pressure from intermediate pressure The back pressure space 77 of pressure increase is set just to be connected to the 2nd supply from the earlier stage of the compression section of discharge chambe 33a, 33b, 33c Portion 69b stablizes the pressure in back pressure space 77 in high pressure later.
Thereby, it is possible to start the ejection process of discharge chambe 33a, 33b, 33c in earlier stage, squit hole 35 can be made Open and close valve 37 sprays the high-pressure refrigerant in discharge chambe 33a, 33b, 33c efficiently fully in earlier stage valve opening, can Seek to improve refrigerant compression power.
In addition, in the present embodiment, the interval 69c between the 1st supply unit 69a and the 2nd supply unit 69b is set It is set to wider than the width in the back pressure space 77 of blade groove 75 but it is also possible to be interval 69c is on the direction of rotation X of rotor 23 The size smaller than the size in back pressure space 77.In this case, back pressure space 77 connection target from high voltage supply portion 69 It when 1st supply unit 69a changes to the 2nd supply unit 69b, and is the phase in back pressure space 77 when back pressure space 77 is across interval 69c The amount Chong Die with interval 69c is reduced for the connection sectional area of each supply unit 69a, 69b.
Since connection sectional area is reduced, when the back pressure of the rotation along with rotor 23, blade 25 to blade groove 75 is empty Between 77 sides submerge, when the volume in back pressure space 77 is reduced, make high pressure in back pressure space 77 to the 1st supply unit 69a, the 2nd supply The efficiency that portion 69b keeps out of the way correspondingly declines with the amount of the volume of reduction.In this case, there are following possibilities: in compression work The later period of sequence sprays in process, and the pressure in back pressure space 77 temporarily rises, and blade 25 presses the inner peripheral surface 33d of cylinder chamber 33 Power excessively increase, resistance to sliding between the inner peripheral surface 33d of blade 25 and cylinder chamber 33 increases.
But will interval 69c configuration in such position, that is, blade 25 be slidingly contacted at along with rotor 23 to When the region of the slip of the protrusion stroke of the blade 25 of the rotation of direction of rotation X minimum (c), back pressure space 77 and interval The position of 69c connection.Therefore, it can prevent the efficiency of keeping out of the way of the high pressure in back pressure space 77 from declining and the pressure in back pressure space 77 Temporarily rise.Therefore, it can prevent the temporary pressurization in the later period, the back pressure space 77 for spraying process of compression section from leading Cause blade 25 the resistance to sliding increase of the inner peripheral surface 33d relative to cylinder chamber 33 and power needed for the rotation of rotor 23 increase, It is able to maintain that the action performance as gas compressor 1.
In addition, in the present embodiment, on the basis of the slip relative to the protrusion stroke of blade groove 75 of blade 25 To determine the region of the inner peripheral surface 33d of the cylinder chamber 33 of 25 sliding contacts of blade when back pressure space 77 is connected to interval 69c.? When decision, with for back pressure space 77 pressure temporary increased permissible range correspondingly, to determine blade 25 The upper limit value of the permissible range of the slip of protrusion stroke relative to blade groove 75.
Also, using the upper limit value of decision as defined threshold value, come determine cylinder chamber 33 inner peripheral surface 33d, blade 25 The slip of prominent stroke is the threshold value such region below.Configuration space 69c as follows is sliding in blade 25 When the region of the dynamic inner peripheral surface 33d for being contacted with the cylinder chamber 33 determined like this, back pressure space 77 is connected to interval 69c.
Interval by carrying out such decision, between back pressure space 77 and the 1st supply unit 69a and the 2nd supply unit 69b It, can be by the temporary pressurization control in back pressure space 77 caused by the reduction of the protrusion stroke of blade 25 during 69c is connected to System is in permissible range.Therefore, the temporary pressurization in the later period of compression section, the back pressure space 77 for spraying process can be prevented Lead to the resistance to sliding increase of the inner peripheral surface 33d relative to cylinder chamber 33 of blade 25 and power needed for the rotation of rotor 23 increases Greatly, it is able to maintain that the action performance as gas compressor 1.
In the present embodiment, high voltage supply slot 69 is divided into two the 1st supplies independent of each other on the X of direction of rotation Portion 69a and the 2nd supply unit 69b.But high voltage supply slot 69 is divided into 3 or more supply units on the X of direction of rotation The present invention can also be applied for situation.In this case, in the interval and cylinder chamber of two supply units adjacent on the X of direction of rotation Relative position between circumferential surface can be applicable in relationship of the invention.
[other embodiments]
In above-mentioned multiple embodiments, the 2nd supply unit 69b of high voltage supply slot 69 is set as in the rotation side of rotor 23 Two adjacent back pressure spaces 77 will not simultaneously be connected to the size of the 2nd supply unit 69b on X.For example, it can be, On the X of direction of rotation, the 2nd supply unit 69b has the space of the size bigger than the size of the 1st supply unit 69a.By doing so, energy Enough make towards high pressure to make the back pressure space 77 of pressure increase from compression from intermediate pressure and the connection with the 1st supply unit 69a The earlier stage of the compression section of room 33a, 33b, 33c is just connected to the 2nd supply unit 69b, later, can be by back pressure space 77 Pressure is stablized in high pressure.
Thereby, it is possible to start the ejection process of discharge chambe 33a, 33b, 33c in earlier stage, squit hole 35 can be made Open and close valve 37 sprays the high-pressure refrigerant in discharge chambe 33a, 33b, 33c efficiently fully in earlier stage valve opening, can Seek to improve refrigerant compression power.
Moreover, in above-mentioned multiple embodiments, the blade in the back pressure space 77 Yu upstream side of blade 25 in order to prevent 25 back pressure space 77 is connected to identical supply unit, and high voltage supply slot 69 is divided into the 1st supply unit on the X of direction of rotation 69a and the case where the 2nd the two supply units of supply unit 69b, are illustrated.But high voltage supply slot 69 is being rotated The case where 3 or more supply units are divided on the X of direction, also can be widely using the present invention.
In this case, height is pressed to from centre in 3 or more supply units and in back pressure space 77 pressure The supply unit for pressing the back pressure space 77 of the state in the way risen to be connected to, as long as being formed as two adjacent on the X of direction of rotation Back pressure space 77 will not be connected to the shape of the supply unit simultaneously, just can also obtain identical with above-mentioned multiple embodiments Effect.
Be formed as on the X of direction of rotation that is, the supply unit that the most upstream side of spinning direction X is located at second at least becomes Two adjacent back pressure spaces 77 will not be connected to the object of the shape of the supply unit simultaneously.Moreover, for from most upstream side The later supply unit of third supply unit, it is empty with back pressure when pressure in back pressure space 77 is from the way that centre presses to high pressure rising Between in the case where 77 connections, also become and be formed as two back pressure spaces 77 adjacent on the X of direction of rotation and will not be connected to simultaneously The object of the shape of the supply unit.
Above embodiments of the present invention are only simple illustration that is for easy understanding of the invention and recording, this hair It is bright to be not limited to the embodiment.Technical scope of the invention is not limited to technology thing specific disclosed in above embodiment , the technical scope of the application can be also contained in from easily derived various modifications and changes disclosed above, substitute technology It is interior.
This application claims be willing to based on Japanese Patent filed on December 24th, 2014 priority of 2014-260491, The priority of 2014-260492 is willing to, based on December 24th, 2014 based on Japanese Patent filed on December 24th, 2014 The Japanese Patent of application is willing to the priority of 2014-260500, the full content of above-mentioned application by referring to and be incorporated into this Specification.
Industrial availability
According to the present invention, it has terminated and the back pressure space of the blade groove of the connection of intermediate pressure supply unit and high voltage supply portion The connection of 1st supply unit, is supplied to high pressure from the 1st supply unit, until the discharge chambe separated by the blade for being incorporated in the blade groove Refrigerant pressure reach maximal pressure.Later, which swims the back pressure of the next blade groove of side in a rotational direction Space is connected to the connection to terminate before the 1st supply unit with the 1st supply unit, and is connected to independent next with the 1st supply unit The 2nd supply unit, be supplied to high pressure again.
Therefore, in the 1st supply for being connected to high voltage supply portion with the back pressure space of the connection of intermediate pressure supply unit that terminated The time point in portion, the leading back pressure space adjacent with the downstream side on the direction of rotation in the back pressure space will not be simultaneously with the 1 Supply unit connection.Therefore, can prevent the pressure in leading back pressure space because chase after from next back pressure space intermediate pressure And temporarily from high drops, the vibration of the blade caused by the temporary decompression in the back pressure space of blade can be prevented Dynamic generation.
Description of symbols
1 gas compressor；2 shells；3 compression units；4 motor parts；5 inverters；7 front covers；9 rear shells；11 suction chambers；In 13 Wall；15,108 discharge chamber；19 compression bodies；21 oil eliminators；23,102 rotor；23a outer peripheral surface；25(25A,25B,25C),103 Blade；27 drive shafts；29,100 cylinder body；31,101 lateral body；31a front side body；Body on rear side of 31b；33,105 cylinder chamber；33a,33b, 33c, 105a, 105b, 105c discharge chambe；33d inner peripheral surface；35 squit holes；37,109 open and close valve；39 inlet holes；41 cylinder side oil supply To path；43 front end faces；47 front side bearings；The oily feed path in 49 front sides；51,113 intermediate pressure feed trough；53,114 high pressures supply To slot；55 front side endless grooves；57 back end surfaces；59 oily supply holes；Oily feed path on rear side of 59a；Oily feed path on rear side of 59b； 61 squit holes；63 rear side bearings；65 rear side access；67 intermediate pressure feed troughs (intermediate pressure supply unit)；69 high voltage supply slots are (high Press supply unit)；The 1st supply unit of 69a (supply unit of upstream side)；The 2nd supply unit of 69b (supply unit in downstream side)；The interval 69c； 71a, 71b high voltage supply access；73 rear side endless grooves；75,106 blade groove；77 (77A, 77B, 77C), 107 back pressure spaces；79 Stator；81 motor rotors；110 suction inlets；O oil；The direction of rotation X.

Claims (7)

1. a kind of gas compressor (1), which is characterized in that
The gas compressor (1) includes
The cylinder body (29) of tubular, it is internal that there is the cylinder chamber (33) that can compress refrigerant；
Lateral body (31a, 31b), is installed on the side of the cylinder body (29), seals the opening of the cylinder chamber (33) of the side；
Rotor (23), the rotation in the cylinder chamber (33), the rotor have multiple leaves spaced apartly on direction of rotation (X) Film trap (75), multiple blade groove (75) is in the opposite with the inner peripheral surface (33d) of the cylinder chamber (33) outer of the rotor (23) Circumferential surface (23a) opening；
Multiple blades (25), multiple blade are accommodated in each blade groove (75) and respectively relative to the outer peripheral surface (23a) Prominent and submerge, multiple blade is slidingly contacted at the inner peripheral surface (33d) of the cylinder chamber (33), and by the inner peripheral surface (33d) and Multiple discharge chambes (33a, 33b, 33c) is separated between the outer peripheral surface (23a) of the rotor (23)；
Intermediate pressure supply unit (67) is formed at least one of described lateral body (31a, 31b), is connected to receiving for self-priming The blade groove (75) for the blade (25) that the discharge chambe (33a, 33b, 33c) for entering process to compression section separates The back pressure space (77) of slot bottom, and will be than the refrigeration of the discharge chambe (33a, 33b, 33c) from inhalation process to compression section The big intermediate pressure of agent pressure is supplied to the back pressure space (77)；And
High voltage supply portion (69) is formed at least one of described lateral body (31a, 31b), whole in the back pressure space (77) It has tied with after the connection of the intermediate pressure supply unit (67), which is connected to receiving will be from compression section to ejection The back pressure space of the blade groove (75) for the blade (25) that the discharge chambe (33a, 33b, 33c) of process separates It (77), and will be than from compression section to the refrigerant pressure of the discharge chambe (33a, 33b, 33c) that sprays process and described The big high voltage supply of intermediate pressure to the back pressure space (77),
The high voltage supply portion (69) is divided into multiple supply units independent of each other on the direction of rotation (X),
The high voltage supply portion (69) includes: the 1st supply unit (69a)；And
The 2nd supply unit positioned at the downstream side of the direction of rotation (X) of the 1st supply unit (69a),
2nd supply unit (69b) is formed as being connected to the 2nd supply in the back pressure space (77) of a blade groove (75) During portion, the 2nd supply unit will not be connected to simultaneously it is adjacent in the upstream side of the direction of rotation (X) and the blade groove (75) Other blade grooves (75) the back pressure space (77) shape, and the high voltage supply portion (69) is formed as simultaneously It is connected to the back pressure space (77) of the blade groove (75) and upstream side and the blade groove at the direction of rotation (X) (75) range of the back pressure space (77) of other the adjacent blade groove (75).
2. gas compressor (1) according to claim 1, which is characterized in that
Adjacent the 1st supply unit (69a) and the 2nd supply unit (69b) are in the rotation on the direction of rotation (X) There is interval, which makes on direction (X): the back pressure space (77) simultaneously with the 1st supply unit (69a) and described When 2nd supply unit (69b) is connected to, connection sectional area between the back pressure space and each supply unit is added up to respectively to each confession More than the minimum path sectional area of the high voltage supply access (71a, 71b) of portion's supply high pressure.
3. gas compressor (1) according to claim 1, which is characterized in that
1st supply unit (69a) and the 2nd supply unit (69b) on the direction of rotation (X) (69c) spaced apart Configuration,
Interval (69c) configuration exists: in the reduction of the protrusion stroke relative to the blade groove (75) of the blade (25) Rate is the rotational position of the defined threshold value rotor (23) below, the interval (69c) and the back pressure space (77) The position of connection.
4. gas compressor (1) according to claim 3, which is characterized in that
The inner peripheral surface (33d) of the cylinder chamber (33) is formed as successively being continuously formed on the direction of rotation (X):
Be slidingly contacted at the protrusion stroke from the blade groove (75) of the blade (25) of the inner peripheral surface (33d) along with The rotation towards the direction of rotation (X) of the rotor (23) and increased region a；
Be slidingly contacted at the protrusion stroke from the blade groove (75) of the blade (25) of the inner peripheral surface (33d) along with The rotation towards the direction of rotation (X) of the rotor (23) and the region b of reduction；
Be slidingly contacted at the protrusion stroke from the blade groove (75) of the blade (25) of the inner peripheral surface (33d) along with The rotation towards the direction of rotation (X) of the rotor (23) and reduce and its slip is smaller than the slip of the region b Region c；And
Be slidingly contacted at the protrusion stroke from the blade groove (75) of the blade (25) of the inner peripheral surface (33d) along with The rotation towards the direction of rotation (X) of the rotor (23) and reduce and its slip is bigger than the slip of the region c And the region d smaller than the slip of the region b,
Interval (69c) configuration exists: when the blade (25) is slidingly contacted at the region c of the inner peripheral surface (33d), The position that the interval (69c) is connected to the back pressure space (77) for the blade groove (75) for accommodating the blade (25).
5. gas compressor (1) according to claim 2, which is characterized in that
1st supply unit (69a) and the 2nd supply unit (69b) on the direction of rotation (X) (69c) spaced apart Configuration,
Interval (69c) configuration exists: in the reduction of the protrusion stroke relative to the blade groove (75) of the blade (25) Rate is the rotational position of the defined threshold value rotor (23) below, the interval (69c) and the back pressure space (77) The position of connection.
6. gas compressor (1) according to claim 5, which is characterized in that
The inner peripheral surface (33d) of the cylinder chamber (33) is formed as successively being continuously formed on the direction of rotation (X):
Be slidingly contacted at the protrusion stroke from the blade groove (75) of the blade (25) of the inner peripheral surface (33d) along with The rotation towards the direction of rotation (X) of the rotor (23) and increased region a；
Be slidingly contacted at the protrusion stroke from the blade groove (75) of the blade (25) of the inner peripheral surface (33d) along with The rotation towards the direction of rotation (X) of the rotor (23) and the region b of reduction；
Be slidingly contacted at the protrusion stroke from the blade groove (75) of the blade (25) of the inner peripheral surface (33d) along with The rotation towards the direction of rotation (X) of the rotor (23) and reduce and its slip is smaller than the slip of the region b Region c；And
Be slidingly contacted at the protrusion stroke from the blade groove (75) of the blade (25) of the inner peripheral surface (33d) along with The rotation towards the direction of rotation (X) of the rotor (23) and reduce and its slip is bigger than the slip of the region c And the region d smaller than the slip of the region b,
Interval (69c) configuration exists: when the blade (25) is slidingly contacted at the region c of the inner peripheral surface (33d), The position that the interval (69c) is connected to the back pressure space (77) for the blade groove (75) for accommodating the blade (25).
7. gas compressor described according to claim 1~any one of 6 (1), which is characterized in that
2nd supply unit (69b) has the ruler bigger than the size of the 1st supply unit (69a) on the direction of rotation (X) Very little space.
CN201580070926.0A 2014-12-24 2015-12-16 gas compressor Expired - Fee Related CN107110158B (en)

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
JP2014-260500 2014-12-24
JP2014-260491 2014-12-24
JP2014260492A JP5878971B1 (en) 2014-12-24 2014-12-24 Gas compressor
JP2014260500A JP5831619B1 (en) 2014-12-24 2014-12-24 Gas compressor
JP2014-260492 2014-12-24
JP2014260491A JP5878970B1 (en) 2014-12-24 2014-12-24 Gas compressor
PCT/JP2015/085193 WO2016104274A1 (en) 2014-12-24 2015-12-16 Gas compressor

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Publication Number Publication Date
CN107110158A CN107110158A (en) 2017-08-29
CN107110158B true CN107110158B (en) 2019-01-22

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EP (1) EP3239530A4 (en)
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WO (1) WO2016104274A1 (en)

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JP6825530B2 (en) * 2017-09-29 2021-02-03 株式会社豊田自動織機 Vane compressor
DE102017128972A1 (en) * 2017-12-06 2019-06-06 Joma-Polytec Gmbh vacuum pump
KR102223283B1 (en) * 2018-11-16 2021-03-05 엘지전자 주식회사 Vain rotary compressor
CN111997898A (en) * 2020-09-10 2020-11-27 常州康普瑞汽车空调有限公司 Backpressure optimization structure and method for rotary vane compressor

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JPH01141391U (en) * 1988-03-23 1989-09-28
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CN107110158A (en) 2017-08-29

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