CN101737325A - Rotary compressor - Google Patents

Rotary compressor Download PDF

Info

Publication number
CN101737325A
CN101737325A CN200910166767A CN200910166767A CN101737325A CN 101737325 A CN101737325 A CN 101737325A CN 200910166767 A CN200910166767 A CN 200910166767A CN 200910166767 A CN200910166767 A CN 200910166767A CN 101737325 A CN101737325 A CN 101737325A
Authority
CN
China
Prior art keywords
slave cylinder
clutch release
release slave
blade
spring
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.)
Granted
Application number
CN200910166767A
Other languages
Chinese (zh)
Other versions
CN101737325B (en
Inventor
寺井利行
岸康弘
土屋直洋
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.)
Hitachi Johnson Controls Air Conditioning Inc
Original Assignee
Hitachi Appliances Inc
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
Application filed by Hitachi Appliances Inc filed Critical Hitachi Appliances Inc
Publication of CN101737325A publication Critical patent/CN101737325A/en
Application granted granted Critical
Publication of CN101737325B publication Critical patent/CN101737325B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/04—Wound springs
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps
    • Y10S417/902—Hermetically sealed motor pump unit

Landscapes

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

Abstract

The present invention provides a rotary compressor which ensures the performance and reliability in an air conditioner and simultaneously realizes miniaturization. A compressing mechanism part (5) of the air conditioner (1) comprises the following components: a working cylinder (51) which is provided with a working cylinder chamber (51a), a blade receiving part (51b) which extends from the working cylinder chamber (51a) to the outside in radial direction, and a spring insertion opening (51c) which extends from an outer peripheral surface to the inside in the radial direction; a roller (52) which is driven to rotate by an eccentric part (4a) of a crank shaft (4); blocking members (53, 54) which are configured with a mode of blocking the working cylinder chamber (51a); blades (55) which are received in the blade receiving part (51b), have front ends that abut against the outer peripheral surface of the roller (52) and move corresponding with the eccentric movement of the roller; coil-shaped springs (56) which are configured in the spring insertion holes (51c) and press the blades (55) on the roller (52). The bottom of each spring insertion hole (51c) is configured to a state that a part opposite with the front end of the spring (56) is actually deepest.

Description

Rotary compressor
Technical field
The present invention relates to rotary compressor, be specially adapted to spring at clutch release slave cylinder and insert in the hole and possess the rotary compressor of the spring of pushing blade.
Background technique
As existing rotary compressor, known have a disclosed technology in TOHKEMY 2003-278679 communique (patent documentation 1).
This rotary compressor possesses following structure in seal container: motor; Bent axle, it is by this motoring and have eccentric part; Compression mechanical part, it drives by eccentric part.This compression mechanical part possesses clutch release slave cylinder, roller, inaccessible parts, blade and spring.
And the clutch release slave cylinder of this compression mechanical part has the clutch release slave cylinder chamber that is arranged on central authorities, the spring patchhole that extends to radially inner side to the blade container that radial outside extends, from outer circumferential face from this clutch release slave cylinder chamber.Roller is configured in the indoor and eccentric part rotary driving by bent axle of clutch release slave cylinder.Inaccessible parts are configured in the axial both sides of clutch release slave cylinder in the mode of inaccessible clutch release slave cylinder chamber.Blade is accommodated in the blade container, and its front end moves in this blade container with the outer circumferential face butt of roller and with the eccentric motion of this roller is corresponding.Spring is disposed at the spring patchhole of clutch release slave cylinder, and by blade is constituted by the spring that is pressed in the coiled type on the roller.The spring patchhole constitutes to the outstanding bottom shape of radially inner side.That is, the processing of spring patchhole is undertaken by drill bit usually, and front end keeps the roughly angle of 90～120 degree, thereby makes the bottom of spring patchhole form cone shape.
[patent documentation 1]: TOHKEMY 2003-278679 communique.
In recent years, along with the significance of environmental protection improves, the inhibition of the use amount of resource becomes important, wish the miniaturization of rotary compressor strongly.When realizing the miniaturization of rotary compressor, there is following problem as can be known.
When making the rotary compressor miniaturization, if carry out similar dwindling, then the clutch release slave cylinder chamber also diminishes, and whenever revolves the spray volume that turns around and tails off, and causes performance to reduce.Like this, there is restriction in clutch release slave cylinder, roller and the blade equidimension that forms compressor, can not carries out miniaturization simply.Therefore,, need guarantee the clutch release slave cylinder chamber size, dwindle the size of clutch release slave cylinder chamber parts on every side simultaneously, particularly, dwindle the outside dimension of clutch release slave cylinder in order to make the rotary compressor miniaturization.
In this case, existing rotary compressor is because the bottom of spring patchhole is coniform recessed, therefore may cause between spring patchhole and the clutch release slave cylinder chamber the seal length size (in other words, sealing area) minimizing, and because the leakage between clutch release slave cylinder chamber and the spring patchhole causes performance to reduce.On the other hand, in order to ensure the seal length size between spring patchhole and the clutch release slave cylinder chamber,, then may cause reliability to reduce owing to not obtaining sufficient spring performance if shorten spring patchhole and spring.
In addition, as realizing miniaturization and guaranteeing to give as security except that the structure of measuring (pressing the amount of removing), in design when to make the ratio of the internal diameter size of clutch release slave cylinder and outside dimension be rotary compressor more than 0.4, if can guarantee fully to give as security the amount of removing and the offset that increases bent axle, then must shorten the radial length of blade container.Therefore, the slide area in the compressor operation between blade and the blade container under the most outstanding state in blade container reduces, and may be difficult to guarantee reliability.Especially, realizing miniaturization and realizing simultaneously having problems under the situation of high capacity.And then, on-stream owing to bear the gas force that the pressure difference because of the two sides of the blade of clutch release slave cylinder chamber produces, so blade tilts from high side to low side in the blade container, slides in the mode of damaging clutch release slave cylinder, may cause the reduction of reliability thus.
Summary of the invention
The objective of the invention is to, provide a kind of and guarantee that performance and reliability and while can realize the rotary compressor of miniaturization.
In order to realize described purpose, the present invention has following structure in seal container: motor; Bent axle, it is by this motoring and have eccentric part; Compression mechanical part, it drives by described eccentric part, described compression mechanical part has: clutch release slave cylinder, it has the clutch release slave cylinder chamber that is arranged on central authorities, from this clutch release slave cylinder chamber to blade container that radial outside extends and the spring patchhole that extends to radially inner side from outer circumferential face; Roller, it is indoor and by described eccentric part rotary driving that it is configured in described clutch release slave cylinder; Inaccessible parts, its mode with the described clutch release slave cylinder of obturation chamber is configured in the axial both sides of described clutch release slave cylinder; Blade, it is accommodated in the outer circumferential face butt of described blade container and its front end and described roller, and corresponding and mobile with the eccentric motion of this roller; The spring of coiled type, its be configured in described spring patchhole and with described blade by being pressed on the described roller, described rotary compressor is characterised in that it is in fact the darkest that the bottom of described spring patchhole constitutes the part relative with described spring front end.
The concrete configuration example of described present invention further optimization is as described below.
(1) ratio of the internal diameter size of described clutch release slave cylinder and outside dimension is more than 0.4, the diameter dimension of described spring patchhole is below 0.5 of axial length dimension of described clutch release slave cylinder, and the ratio of the length dimension of the blade slip surface under the outstanding state of the impeller clearance size in the described blade container and the maximum of described blade is below 0.0025.
(2) contact of the bottom of the described spring patchhole spring front end avoiding inserting at outer circumferential side, simultaneously central side be with outer circumferential side on an equal basis with the interior degree of depth.
(3) recess of end of the described spring of assembling is set at described blade, the axial dimension of described recess is below 0.6 of height dimension of described spring.
(4) plane of inclination of chamfering is set at the pressing chamber opposition side of the slip surface that slides with described clutch release slave cylinder of described blade.
(5) number of turn of connecting airtight coiling portion of described spring is below 4 circles.
(6) the coiling portion of connecting airtight of described spring is shaped as roughly smooth-shaped.
According to described rotary compressor of the present invention, can guarantee performance and reliability, and can realize miniaturization simultaneously.
Description of drawings
Fig. 1 is the sectional arrangement drawing of the longitudinal type rotary compressor of the 1st mode of execution of the present invention.
Fig. 2 is the stereogram in the central cross section of the clutch release slave cylinder of Fig. 1.
Fig. 3 is the stereogram of the blade of Fig. 1.
Fig. 4 is the plan view of sliding mode of blade of the longitudinal type rotary compressor of explanatory drawing 1.
Fig. 5 is that the variation of wear extent of expression the 1st mode of execution is with respect to the figure of the variation of the ratio of the length dimension of the slip surface of the outstanding state of the maximum of impeller clearance size and blade.
Fig. 6 is that the variation of wear extent of expression the 1st mode of execution is with respect to the figure of the variation of the ratio of T portion height and clutch release slave cylinder height.
Fig. 7 is the sectional drawing of part of clutch release slave cylinder of the rotary compressor of expression the 2nd mode of execution of the present invention.
Fig. 8 is the stereogram of blade of the rotary compressor of expression the 3rd mode of execution of the present invention.
Symbol description: 1-rotary compressor, 2-seal container, 3-motor, 4-bent axle, the 4a-eccentric part, 5-compression mechanical part, 6-lubricant oil, 31-stator, the 32-rotor, 51-clutch release slave cylinder, 51a-clutch release slave cylinder chamber, 51b-blade container, 51c-spring patchhole, 52-roller, 53, the inaccessible parts of 54-, 55-blade, the 55a-spring is installed recess, 56-spring, 57-outlet valve, the 58-fixing bolt, 59-suction pipe, 60-discharge tube.
Embodiment
Below, use accompanying drawing that a plurality of mode of executions of the present invention are described.The same-sign of the figure of each mode of execution is represented identical or suitable structure.
(the 1st mode of execution)
Use Fig. 1 the longitudinal type rotary compressor of the 1st mode of execution of the present invention to be described to Fig. 6.Fig. 1 is the sectional arrangement drawing of the longitudinal type rotary compressor of present embodiment, Fig. 2 is the stereogram in the central cross section of the clutch release slave cylinder of Fig. 1, Fig. 3 is the stereogram of the blade of Fig. 1, Fig. 4 is the plan view of sliding mode of blade of the longitudinal type rotary compressor of explanatory drawing 1, Fig. 5 is the figure of the variation of expression wear extent with respect to the variation of the ratio of the length dimension of the slip surface of the outstanding state of maximum of the impeller clearance size of present embodiment and blade, and Fig. 6 is the figure of the variation of expression wear extent with respect to the variation of the ratio of the T portion height of present embodiment and clutch release slave cylinder height.The rotary compressor of present embodiment is as the constituting component of the refrigeration cycle of refrigerator, air regulator, heat-pump hot water supply apparatus etc. and use.
Rotary compressor 1 has following structure in seal container 2: motor 3; Bent axle 4, it is by these motor 3 drivings and have eccentric part 4a; Compression mechanical part 5, it drives by this eccentric part 4a; Lubricant oil 6.This rotary compressor 1 is characterised in that than existing technology miniaturization more, particularly pathization.
It is cylindric that seal container 2 forms lengthwise, at bottom storage lubricant oil 6.The pasta of this lubricant oil 6 stores in the mode of the height of the centre that is positioned at clutch release slave cylinder 51.
Motor 3 has and is fixed on the stator 31 in the seal container 2 and rotatably is configured in the interior rotor 32 of this stator 31.Motor 3 is configured in the top in the seal container 2.
The top of bent axle 4 is inserted in the rotor 32 and is fixed on the rotor 32, and bent axle 4 is with rotor 32 rotations thus.Insert in the compression mechanical part 5 bottom of bent axle 4, makes roller 52 eccentric rotation, portions of drive compression mechanism 5 thus by eccentric part 4a.
Compression mechanical part 5 has following structure: clutch release slave cylinder 51; Roller 52; Inaccessible parts 53,54, blade 55, spring 56, outlet valve 57, fixing bolt 58.This compression mechanical part 5 is configured in the bottom in the seal container 2.
The basic shape of clutch release slave cylinder 51 is the drum of heavy wall, is configured in the lower surface of inaccessible parts 53 and passes through fixing bolt 58 fixing.Clutch release slave cylinder 51 has clutch release slave cylinder chamber 51a, blade container 51b, spring patchhole 51c.
Clutch release slave cylinder chamber 51a is arranged on the central authorities of clutch release slave cylinder 51, is formed by the circular inner peripheral surface of clutch release slave cylinder 51.In the present embodiment, the ratio of the internal diameter size of clutch release slave cylinder 51 shown in Figure 2 (diameter dimension of clutch release slave cylinder chamber 51a) d and outside dimension D is more than 0.4, thereby can realize miniaturization and guarantee to give as security the amount of removing simultaneously.
Blade container 51b forms from the narrow groove of clutch release slave cylinder chamber 51a to the linearly extension of radial outside.Spring patchhole 51c forms the hole of the circle of extending to radially inner side from the outer circumferential face of clutch release slave cylinder 51, and is set to have the part that repeats with blade container 51b.
Roller 52 is configured in the 51a of clutch release slave cylinder chamber, and passes through the eccentric part 4a rotary driving of bent axle 4.Divided by blade 55 by the space that the inner peripheral surface of the outer circumferential face of roller 52 and clutch release slave cylinder 51 forms, form suction chamber and pressing chamber in the both sides of blade 55.Here, the refrigerant gas of refrigeration cycle is inhaled into suction chamber by suction pipe 59.This suction chamber makes at this pressing chamber refrigerant compressed gas and discharges in seal container 2 by outlet valve 57 to the pressing chamber transition.The refrigerant gas of discharging in seal container 2 is back in the outside refrigeration cycle by discharge tube 60.
Inaccessible parts 53,54 are configured in the axial both sides of clutch release slave cylinder 51 in the mode of inaccessible clutch release slave cylinder chamber 51a.Inaccessible parts 53 are by being fixedly welded on seal container 2.Then, clutch release slave cylinder 51 is fixed in inaccessible parts 53 by fixing bolt 58, and inaccessible parts 54 are fixed in clutch release slave cylinder 51.Therefore, inaccessible parts 53, clutch release slave cylinder 51 and inaccessible parts 54 are supported successively with respect to seal container 2.Also have, inaccessible parts 53 constitute the main bearing of bent axle 4, and inaccessible parts 54 constitute the supplementary bearing of bent axle 4.
Blade 55 is accommodated in blade container 51b, and its front end radially moves in the 51b of this blade container with the outer circumferential face butt of roller 52 and with the eccentric motion of this roller 52 is corresponding.
Spring 56 is made of the spring of coiled type, so that blade 55 is disposed at spring patchhole 51c by the mode that is pressed on the roller 52.Spring 56 has the not shown coiling portion of connecting airtight, and this number of turn of connecting airtight coiling portion for example is made as 3 circles below 4 circles.In order in the size that limits, spring part to be set, to be made as below 4 circles with the length of connecting airtight coiling portion that elastic force has nothing to do, thus in the size that limits, can guarantee between spring patchhole 51c and the clutch release slave cylinder chamber 51a the seal length size (in other words, sealing area), and can increase the effective turn of spring part, thereby can improve degrees of freedom, can be implemented in spring patchhole 51c internal fixation spring 56 in addition simultaneously the design of spring part.Connect airtight level and smooth (the ス ト レ one ト) shape of being shaped as roughly of coiling portion by making in addition, even the influence of the inclination when the Duan coiling portion of connecting airtight also can reduce insertion thus.
Above-mentioned spring patchhole 51c forms by End Milling Process, its bottom constitutes tabular surface, thus near the front end of the inserting side of spring 56, constitute the actual deepest part of spring patchhole 51c, with the inboard suitable part of spring 56, spring patchhole 51c constitutes and the equal degree of depth of described front end, perhaps so long as the shape of interfering with spring not also can be more shallow structure.By described simple structure, even dwindle the outside dimension of clutch release slave cylinder 51, also can guarantee the seal length size between spring patchhole 51c and the clutch release slave cylinder chamber 51a fully, can reduce the leakage of sealing part thus, the performance that can suppress to cause because of leakage reduces, and can bring into play the function of spring 56 fully, thereby guarantee reliability.
The sealing part is low-temp low-pressure zone and the High Temperature High Pressure zone in pressure span in the compression way and the delivery pressure zone in the container and the part that seals that separates the suction nip territory in the 51a of clutch release slave cylinder chamber for the compressor in the running.Partly produced under the situation of leaking in sealing,, caused that the heating or the pressure that suck gas rise, and therefore cause performance to reduce because the gas of High Temperature High Pressure flows into to the pressing chamber zone.
In the present embodiment, making the diameter dimension a of spring patchhole 51c shown in Figure 2 is below 0.5 of H of axial length dimension (being thickness size) of clutch release slave cylinder 51.Like this, by reducing the diameter dimension a of spring patchhole 51c, can enlarge height dimension (in other words, enlarge sealing area), thereby it is lower the face in the T of blade 55 one can be constrained system ground as the T portion of the sealing surface of the blade container 51b of the above-below direction that is positioned at spring patchhole 51c.Carried out after the various experiments as can be known, along with the ratio of the height dimension H of the height dimension of the T portion of blade container 51b and clutch release slave cylinder 51 diminishes, the wearing and tearing quantitative change of blade slide part is big, as shown in Figure 6, if make this ratio be lower than 0.5, then the wear extent of blade slide part becomes big sharp.In other words as can be known, this ratio can obtain the wear extent region of stability 0.5 when above.
And then as if blade 55 over-tilting in the 51b of the blade container of clutch release slave cylinder 51, then the way of contact of clutch release slave cylinder 51 and blade 55 is contacted or puts the possibility rising of state of contact near line by surface contact state in the running of compressor.As shown in Figure 4, the impeller clearance size of blade container 51b is made as Δ V, and the length dimension of the blade slip surface of blade 55 under the outstanding state of maximum of roller side is made as E.Here as can be known, the wear extent that becomes big blade slide part along with Δ V/E increases, if Δ V/E surpasses 0.0025, then the wear extent of blade slide part becomes big sharp especially.In other words, be 0.0025 when following at Δ V/E, can obtain the wear extent region of stability.
In addition, the height dimension b that the spring of blade 55 preferred shown in Figure 3 is installed recess 55a is made as below the diameter dimension a of spring patchhole 51c, and in other words, preferred heights size b is below 0.5 of height dimension H of clutch release slave cylinder 51.Thus, can have the relation identical with relation shown in Figure 6.As shown in Figure 3, even near the part the end is 0.6 with inferior degree when recess being installed being cone-shaped,, also can obtain same effect by disposing main scope in the part below 0.5.
According to present embodiment, even make rotary compressor 1 miniaturization, also can guarantee the seal length of clutch release slave cylinder 51 and blade 55, thereby guarantee the good sliding mode of blade 55 and clutch release slave cylinder 51.Thus, can realize the rotary compressor 1 of low cost and high reliability.Along with the miniaturization of rotary compressor 1, also can realize the miniaturization of completed knocked down products, therefore can contribute to the saving resource in making, the reduction of carriage load etc.
(the 2nd mode of execution)
Next, use Fig. 7 that the rotary compressor of the 2nd mode of execution of the present invention is described.Fig. 7 is the sectional drawing of part of clutch release slave cylinder of the rotary compressor of expression the 2nd mode of execution of the present invention.The 2nd mode of execution is different with the 1st mode of execution aspect next narrating, and other aspects and the 1st mode of execution are basic identical, and therefore the repetitive description thereof will be omitted.
In the 2nd mode of execution, be arranged at the bottom of forward end of the spring patchhole 51c of clutch release slave cylinder 51, by the peripheral part 51c1 of the end of assembling spring 56 and in the end of this spring 56 side-prominent central part 51c2 constitute.According to the 2nd mode of execution, except that sealing improves, also have the effect of the area of contact that increases blade 55 and clutch release slave cylinder 51, and help reliability to improve.Along with the degree of the miniaturization of compressor further develops and the restriction of size becomes big, the effect of the 2nd mode of execution is more obvious.
(the 3rd mode of execution)
Next, use Fig. 8 that the rotary compressor of the 3rd mode of execution of the present invention is described.Fig. 8 is the stereogram of blade of the rotary compressor of expression the 3rd mode of execution of the present invention.The 3rd mode of execution is different with the 1st mode of execution aspect next narrating, and other aspects and the 1st mode of execution are basic identical, and therefore the repetitive description thereof will be omitted.
In the 3rd mode of execution, the plane of inclination of cone-shaped is set in the pressing chamber opposition side end with slip surfaces clutch release slave cylinder 51 slips blade 55.Thus, slide in the 51b of blade container even blade 55 is in the state of inclination, the face that also can suppress the blade sliding parts presses liter, can realize the slide type of approaching face contact.Also have, also have effect even the angle of cone-shaped is very little, but preferred surpass according to the gap of blade 55 in the 51b of blade container the angle that can tilt.

Claims (8)

1. rotary compressor, it has in seal container: motor; Bent axle, it is by this motoring and have eccentric part; Compression mechanical part, it is driven by described eccentric part,
Described compression mechanical part has: clutch release slave cylinder, it has the clutch release slave cylinder chamber of being located at central authorities, from this clutch release slave cylinder chamber to blade container that radial outside extends and the spring patchhole that extends to radially inner side from outer circumferential face; Roller, it is indoor and by described eccentric part rotary driving that it is configured in described clutch release slave cylinder; Inaccessible parts, its mode with the described clutch release slave cylinder of obturation chamber is configured in the axial both sides of described clutch release slave cylinder; Blade, it is accommodated in the outer circumferential face butt of described blade container and its front end and described roller, and corresponding with the eccentric motion of this roller and move; The spring of coiled type, its be configured in described spring patchhole and with described blade by being pressed on the described roller,
Described rotary compressor is characterised in that,
It is in fact the darkest that the bottom of described spring patchhole constitutes the part relative with described spring front end.
2. rotary compressor according to claim 1 is characterized in that,
The ratio of the internal diameter size of described clutch release slave cylinder and outside dimension is more than 0.4, the diameter dimension of described spring patchhole is below 0.5 of axial length dimension of described clutch release slave cylinder, and the ratio of the length dimension of the blade slip surface under the outstanding state of the impeller clearance size in the described blade container and the maximum of described blade is below 0.0025.
3. rotary compressor according to claim 1 and 2 is characterized in that,
The bottom of described spring patchhole forms tabular surface by End Milling Process.
4. rotary compressor according to claim 1 and 2 is characterized in that,
The bottom of spring patchhole comprises: the peripheral part of assembling the end of described spring; Side-prominent central part in the end of described spring.
5. rotary compressor according to claim 2 is characterized in that,
At pack into the recess of end of described spring of described blade setting,
The axial dimension of described recess is below 0.6 of height dimension of described clutch release slave cylinder.
6. rotary compressor according to claim 2 is characterized in that,
The plane of inclination of chamfering is set at the pressing chamber opposition side with slip surface described clutch release slave cylinder slip described blade.
7. rotary compressor according to claim 1 and 2 is characterized in that,
The number of turn of connecting airtight coiling portion of described spring is below 4 circles.
8. rotary compressor according to claim 7 is characterized in that,
The coiling portion of connecting airtight of described spring is a smooth-shaped roughly.
CN2009101667670A 2008-11-20 2009-08-18 Rotary compressor Active CN101737325B (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008296343A JP5079670B2 (en) 2008-11-20 2008-11-20 Rotary compressor
JP2008-296343 2008-11-20

Publications (2)

Publication Number Publication Date
CN101737325A true CN101737325A (en) 2010-06-16
CN101737325B CN101737325B (en) 2011-12-14

Family

ID=42280889

Family Applications (1)

Application Number Title Priority Date Filing Date
CN2009101667670A Active CN101737325B (en) 2008-11-20 2009-08-18 Rotary compressor

Country Status (3)

Country Link
JP (1) JP5079670B2 (en)
KR (1) KR101172570B1 (en)
CN (1) CN101737325B (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105673504A (en) * 2016-03-21 2016-06-15 珠海格力节能环保制冷技术研究中心有限公司 Compressor and cylinder assembly thereof

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102333957A (en) * 2010-02-24 2012-01-25 松下电器产业株式会社 Rotary compressor
WO2014155803A1 (en) * 2013-03-27 2014-10-02 東芝キヤリア株式会社 Rotary compressor and refrigeration cycle device
CN108252910B (en) * 2017-11-30 2024-06-18 刘悦吟 A kind of compressor
CN112283109A (en) * 2020-11-13 2021-01-29 比泽尔旋转压缩机(江苏)有限公司 Air cylinder assembly with double-spring structure and using method thereof
JP2023180461A (en) * 2022-06-09 2023-12-21 三菱重工サーマルシステムズ株式会社 rotary compressor

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5620795A (en) 1979-07-28 1981-02-26 Toshiba Corp Rotary compressor
JPS56145691U (en) * 1980-04-02 1981-11-02
JPH07208364A (en) * 1994-01-13 1995-08-08 Sanyo Electric Co Ltd Rotary electric-driven compression device
JP3718027B2 (en) * 1997-03-31 2005-11-16 東芝キヤリア株式会社 Rotary compressor
JP3967474B2 (en) * 1998-09-10 2007-08-29 東芝キヤリア株式会社 Rotary compressor
JP3867006B2 (en) * 2002-04-12 2007-01-10 東芝キヤリア株式会社 Rotary compressor
JP2005299490A (en) 2004-04-12 2005-10-27 Matsushita Electric Ind Co Ltd Manufacturing method of refrigerant compressor
JP2006291799A (en) * 2005-04-08 2006-10-26 Matsushita Electric Ind Co Ltd Sealed rotary compressor
CN1896531A (en) * 2005-07-12 2007-01-17 乐金电子(天津)电器有限公司 Blade spring arrangement of rotary compressor
CN201037461Y (en) * 2007-04-29 2008-03-19 上海日立电器有限公司 Rotary piston compressor with stage-shape spring hole

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105673504A (en) * 2016-03-21 2016-06-15 珠海格力节能环保制冷技术研究中心有限公司 Compressor and cylinder assembly thereof
CN105673504B (en) * 2016-03-21 2018-05-18 珠海格力节能环保制冷技术研究中心有限公司 Compressor and its cylinder assembly

Also Published As

Publication number Publication date
CN101737325B (en) 2011-12-14
KR101172570B1 (en) 2012-08-08
KR20100056959A (en) 2010-05-28
JP5079670B2 (en) 2012-11-21
JP2010121546A (en) 2010-06-03

Similar Documents

Publication Publication Date Title
CN101737325B (en) Rotary compressor
EP2177765B1 (en) Scroll compressor and refrigerating machine having the same
JP6156697B2 (en) Rotary compressor with two cylinders
JP3904221B2 (en) Fluid machinery and refrigeration cycle apparatus
US7780427B2 (en) Two-stage rotary compressor
CN102971537B (en) Rotary compressor
CN210715092U (en) Electric compressor device
JP5905005B2 (en) Multi-cylinder rotary compressor and refrigeration cycle apparatus
EP3163084B1 (en) Rotary compressor having two cylinders
KR101510697B1 (en) Rotation shaft and hermetic compressor having the same and refrigerator having the same
US20100089093A1 (en) Scroll compressor and refrigerating machine having the same
CN105822545A (en) Scroll compressor
KR20180080885A (en) Rotary compressor
CN104093986B (en) Scroll compressor
WO2015114883A1 (en) Hermetic compressor
CN104819154A (en) Hermetic Compressor
JP7336052B2 (en) compressor
CN104595183A (en) Compressor with unloader counterweight assembly
JP2013204488A (en) Scroll type fluid machine
KR102547592B1 (en) Vane rotary compressor
KR101587165B1 (en) Scoroll compressor and refrigerator having the same
JP7218195B2 (en) rotary compressor
JP2007270818A (en) Fluid machinery and refrigerating cycle apparatus
CN105649984A (en) Compressing mechanism and low-backpressure rotary compressor
KR20090129820A (en) Compressing mechanism for scroll compressor

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C14 Grant of patent or utility model
GR01 Patent grant
C41 Transfer of patent application or patent right or utility model
TR01 Transfer of patent right

Effective date of registration: 20160826

Address after: Hongkong aoteng Plaza No. 8 Chinese Kowloon Linze street 12 floor

Patentee after: Johnson Controls Hitachi air conditioning technology (Hongkong) Co., Ltd.

Address before: Tokyo, Japan

Patentee before: Hitachi Appliances Inc.

TR01 Transfer of patent right

Effective date of registration: 20180705

Address after: Tokyo, Japan, Japan

Patentee after: Hitachi Johnson Controls Air Conditioning Co., Ltd.

Address before: Hongkong aoteng Plaza No. 8 Chinese Kowloon Linze street 12 floor

Patentee before: Johnson Controls Hitachi air conditioning technology (Hongkong) Co., Ltd.

TR01 Transfer of patent right