WO2022057063A1 - 涡旋压缩机 - Google Patents

涡旋压缩机 Download PDF

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Publication number
WO2022057063A1
WO2022057063A1 PCT/CN2020/128536 CN2020128536W WO2022057063A1 WO 2022057063 A1 WO2022057063 A1 WO 2022057063A1 CN 2020128536 W CN2020128536 W CN 2020128536W WO 2022057063 A1 WO2022057063 A1 WO 2022057063A1
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WO
WIPO (PCT)
Prior art keywords
scroll
guide ring
scroll compressor
main bearing
flange portion
Prior art date
Application number
PCT/CN2020/128536
Other languages
English (en)
French (fr)
Inventor
朱伟
王石
胡小伟
沙海天
Original Assignee
艾默生环境优化技术(苏州)有限公司
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 CN202010997708.4A external-priority patent/CN114251261A/zh
Priority claimed from CN202022080759.9U external-priority patent/CN212479578U/zh
Application filed by 艾默生环境优化技术(苏州)有限公司 filed Critical 艾默生环境优化技术(苏州)有限公司
Publication of WO2022057063A1 publication Critical patent/WO2022057063A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing

Definitions

  • the present disclosure relates to a scroll compressor, and more particularly, to a holding mechanism of a fixed scroll.
  • a scroll compressor generally includes a casing, a drive mechanism accommodated in the casing, a scroll mechanism driven by the drive mechanism, a main bearing housing supporting the scroll mechanism, and the like.
  • the scroll mechanism generally includes an orbiting scroll and a fixed scroll that mesh with each other.
  • the fixed scroll is positioned in the compressor by a retention mechanism.
  • the holding mechanism needs to regulate the movement of the scroll at the upper radial limit and center the radial direction of the fixed scroll; on the other hand, the holding mechanism can allow the fixed scroll to move axially within a certain range, so as to provide Scroll compressors provide some axial flexibility.
  • a common way of retaining the fixed scroll in the prior art is: a lug is provided on the outer periphery of the fixed scroll, a through hole is formed in the lug, and a threaded hole is formed in the arm of the main bearing seat, Bolts with guide sleeves hold the fixed scroll and the main bearing housing together, enabling radial centering of the fixed scroll. Since the through holes formed in the lugs of the fixed scroll can slide in the axial direction along the guide sleeve, the fixed scroll is allowed to move slightly axially relative to the main bearing housing.
  • a guide ring is arranged on the outer periphery of the fixed scroll, a through hole is arranged in the guide ring, and a bolt is used to pass through the through hole in the guide ring and screw it in the guide ring. in the threaded hole in the main bearing housing.
  • the guide ring can radially limit the fixed scroll and allow the fixed scroll to move within a certain range in the axial direction.
  • the first way of retaining the fixed scroll requires processing lugs and through holes on the fixed scroll and using guide sleeves and bolts together, which will increase the radial size of the fixed scroll and increase the size of the fixed scroll. Increases assembly cost and assembly time.
  • the second way of retaining requires machining the guide ring with structural features matching the fixed component (such as the main bearing seat) to realize the radial centering of the guide ring, which also increases the processing difficulty and processing cost of the compressor. Accordingly, there is a need for improved retention of fixed scroll components.
  • the purpose of the present disclosure is to provide a scroll compressor with a new fixed scroll holding mechanism, which can not only realize the radial limit of the fixed scroll, but also allow the fixed scroll to be in the position of the fixed scroll relative to the main bearing seat. Axial movement within a certain range, and simple processing, easy installation, and material saving.
  • a scroll compressor includes: a casing, a scroll mechanism, and a main bearing seat, the scroll mechanism includes a fixed scroll, and the fixed scroll includes an end plate, A scroll extending from the end plate and an outer peripheral wall, the outer peripheral wall is provided on the outer periphery of the scroll, the main bearing housing supports the scroll mechanism, wherein the scroll compressor further includes a retaining mechanism and a locating pin, the retaining mechanism is arranged around the outer peripheral wall to restrict The radial movement of the fixed scroll, the locating pin is connected to the first mounting hole of the retaining mechanism and the second mounting hole of the main bearing seat and is arranged between the retaining mechanism and the main bearing seat in the axial direction, thereby determining the relative relationship of the retaining mechanism to the main bearing seat. Axial position of the main bearing housing.
  • the retaining mechanism includes a guide ring that fits radially with the outer peripheral wall to guide the axial movement of the fixed scroll.
  • the holding mechanism further includes a muffler cover that divides the inner space of the scroll compressor into a low pressure region and a high pressure region, and the guide ring is formed separately from the muffler cover.
  • the muffler cover is connected with the guide ring by interference or by fasteners, so that the guide ring is fixed between the positioning pin and the muffler cover.
  • the sound-absorbing cover is in clearance fit with the guide ring, the guide ring and/or the sound-absorbing cover including an outer flange portion extending radially outward, the outer flange portion being fixedly connected to the housing.
  • the housing includes a housing body and a top cover, and: the outer flange portion of the guide ring is fixedly connected between the housing body and the top cover in the axial direction; or the outer flange portion of the guide ring is connected to the sound-absorbing The outer flange portion of the cover is fixedly connected together in the axial direction between the housing body and the top cover.
  • the guide ring or the muffler cover includes an inner flange portion extending radially inward, an abutting portion is formed at the fixed scroll, and there is a predetermined distance in the axial direction between the inner flange portion and the abutting portion,
  • the fixed scroll can move axially within a range defined by a predetermined distance.
  • the holding mechanism further includes a muffler cover that divides the inner space of the scroll compressor into a low-pressure area and a high-pressure area, the holding mechanism is integrally formed by a guide ring and the muffler cover, and the holding mechanism includes an outer radially extending outer cover.
  • the scroll is capable of axial movement within a range defined by a predetermined distance.
  • the housing includes a housing body and a top cover, and the outer flange portion of the retaining mechanism is fixedly connected between the housing body and the top cover in the axial direction.
  • the positioning pins are at least three positioning pins distributed in the circumferential direction.
  • the positioning pin is configured as a stepped pin with a first stepped portion and/or a second stepped portion, the first stepped portion abuts against the end surface of the holding mechanism provided with the first mounting hole, and the second stepped portion is in contact with the main bearing.
  • the end face of the seat provided with the second mounting hole abuts.
  • the stepped pin is an integral pin formed in one piece, or the stepped pin is a split pin including a pin body and a sleeve sleeved on the pin body.
  • the fixed scroll of the fixed scroll realizes radial centering and axial flexibility through a retaining mechanism, and the retaining mechanism is connected to the main bearing seat through a positioning pin to realize its radial centering and axial positioning, Therefore, the processing of the matching parts of the holding mechanism and the main bearing seat caused by the direct cooperation between the holding mechanism and the main bearing seat is avoided, materials are saved, and the difficulty of processing and installation is reduced; the holding mechanism can be integrally formed, thereby simplifying the installation process.
  • FIG. 1 is a partial longitudinal cross-sectional view of a scroll compressor according to a first exemplary embodiment of the present disclosure
  • FIG. 2 is a schematic perspective view of a portion of a scroll compressor according to the first exemplary embodiment of the present disclosure
  • FIG. 3 is a cross-sectional view showing a cross section of the scroll mechanism of the scroll compressor according to the first exemplary embodiment of the present disclosure
  • FIG. 4 is an exploded perspective view of a portion of a scroll compressor according to the first exemplary embodiment of the present disclosure
  • FIG. 5 is a partial detail longitudinal cross-sectional view of a scroll compressor showing a retention mechanism of the scroll compressor according to the first exemplary embodiment of the present disclosure
  • FIG. 6 is a schematic perspective view of a stepped pin according to the first exemplary embodiment of the present disclosure
  • Figures 7a, 7b and 7c respectively show a schematic perspective view of a step pin and its constituent parts according to the second exemplary embodiment of the present disclosure
  • FIG. 8 is a partial longitudinal cross-sectional view of a scroll compressor according to a third exemplary embodiment of the present disclosure.
  • FIG. 9 is a partial longitudinal cross-sectional view of a scroll compressor according to a fourth exemplary embodiment of the present disclosure.
  • FIG. 10 is a partial longitudinal cross-sectional view of a scroll compressor according to a fifth exemplary embodiment of the present disclosure.
  • FIG. 11 is a partial longitudinal sectional view of a scroll compressor according to a comparative example of the present disclosure.
  • FIGS. 12 and 13 are schematic perspective views of a main bearing seat and a guide ring of a scroll compressor according to a comparative example of the present disclosure, respectively.
  • FIG. 1 is a partial longitudinal cross-sectional view of a scroll compressor according to a first exemplary embodiment of the present disclosure.
  • the scroll compressor 10 mainly includes a casing 20 , a scroll mechanism, a main bearing seat 50 and a driving mechanism (not shown).
  • the housing 20 generally includes a generally cylindrical housing body 26, a top cover 22, and a bottom cover (not shown) that form a complete shell, such as by welding body 20.
  • the scroll compressor 20 is also provided with a muffler cover 24 located between the casing body 26 and the top cover 22 , thereby dividing the compressor interior space into a low pressure region 14 and a high pressure region 12 .
  • the working fluid enters the low pressure area 12 through the suction port fitting 29 provided on the housing body 26 , enters the high pressure area 12 after being compressed by the scroll mechanism, and is discharged to the scroll compressor 10 through the exhaust port fitting 28 provided on the top cover 22 . outside.
  • the scroll mechanism includes a fixed scroll 30 and a movable scroll 40 .
  • the scroll mechanism is driven by the drive mechanism. Specifically, when the driving shaft of the driving mechanism rotates, the movable scroll 40 can be driven via the crank pin of the driving shaft, and the movable scroll 40 can be opposed to the movable scroll 40 due to the Oldham slip ring 80 coupled with the movable scroll 40 and the fixed scroll 30
  • the fixed scroll 30 performs translational rotation.
  • the axis of the movable scroll 40 orbits in a circular orbit relative to the axis of the fixed scroll 30, but both the movable scroll 40 and the fixed scroll 30 themselves do not rotate around their respective axes.
  • the scroll mechanism is supported by the main bearing seat 50 , which is fixedly connected to the casing body 26 by means such as riveting or is integrally formed with the casing body 26 .
  • the fixed scroll 30 includes an end plate 31 and a spiral wrap 32 extending downward from one side of the end plate 31 .
  • the wrap 32 of the fixed scroll 30 and the wrap 42 of the movable scroll 40 mesh with each other, thus forming a series of compression chambers therebetween for compressing a fluid such as a refrigerant.
  • the fixed scroll 30 also includes a substantially cylindrical outer peripheral wall 33 extending downward from the end plate 31 and provided on the outer periphery of the wrap 32 of the fixed scroll 30 .
  • the fixed scroll 30 is positioned in the scroll compressor 10 by a retaining mechanism.
  • the retention mechanism may include a guide ring 60 . 2 and 3 , the guide ring 60 is arranged around the outer peripheral wall 33 of the fixed scroll 30 .
  • the main bearing seat 50 includes a base and three bosses 52 extending from one side of the base toward the guide ring 60 (upward), and the three bosses 52 are circumferentially distributed on the main bearing seat 50 .
  • the positioning pin 70 is arranged between the guide ring 30 and the boss portion 52 of the main bearing seat 50 in the axial direction. Axial position of bearing housing 50 . It can be understood by those skilled in the art that the number of the boss portions 52 and the positioning pins 70 is not limited to the three shown in the figures, and may be more than three.
  • the guide ring 60 includes a substantially annular ring body 61 , an inner flange portion 68 extending radially inward from the inner side wall of the ring body 61 , and an axially extending from the upper end face of the ring body 61 .
  • the upper flange portion 64 extending upward.
  • the guide ring 60 is also provided with a first mounting hole 66 at a position corresponding to the positioning pin 70 on the lower end surface of the ring body 61 .
  • a second mounting hole 54 for receiving the positioning pin 70 is formed in the boss portion 52 of the main bearing seat 50, the second mounting hole 54 is axially aligned with the first mounting hole 66, and one end of the positioning pin 70 is inserted into the guide ring In the first mounting hole 66 of the main bearing seat 50 , the other end is inserted into the second mounting hole 54 of the main bearing seat 50 , so as to connect the guide ring 60 to the main bearing seat 50 . Since the boss portion 52 of the main bearing seat 50 and the second mounting holes 54 thereof are distributed in the circumferential direction, the guide ring 60 positioned by the positioning pin 70 can realize the radially centered installation. Those skilled in the art can understand that the main bearing seat 50 may also not include the boss portion 52 , but the positioning pin 70 is directly connected to the main bearing seat 50 .
  • the positioning pin 70 is configured as a stepped pin having a stepped portion 74 .
  • the positioning pin 70 includes a first diameter portion 71 , a second diameter portion 72 and a third diameter portion 73 .
  • the diameters of the second diameter portion 72 and the third diameter portion 73 are both smaller than the diameter of the first diameter portion 71 .
  • the second diameter portion 72 and the third diameter portion 73 are respectively formed at both ends of the positioning pin 70 , and the first diameter portion 72 is formed at the middle of the positioning pin 70 , so that the second diameter portion 72 is connected to the first diameter portion 71 .
  • a first stepped portion 74 and a second stepped portion 75 are formed at the junction of the third diameter portion 73 and the first diameter portion 71 , respectively.
  • the second diameter portion 72 is matched with the first mounting hole 66 of the guide ring 60
  • the third diameter portion 73 is matched with the second mounting hole 54 of the main bearing seat 60 , so that when the second diameter portion at both ends of the positioning pin 70 is matched 72 and the third diameter portion 73 are inserted into the axially aligned first mounting hole 66 and the second mounting hole 54, respectively, the first step portion 74 and the ring body 61 of the guide ring 60 are provided with a first mounting hole.
  • the lower end face of the guide ring 66 abuts against the second step portion 75 and the upper end face of the boss portion 52 of the main bearing seat 50 that is provided with the second mounting hole 54 .
  • the position is determined by locating pins 70 .
  • the axial distance between the lower end surface of the ring body 61 of the guide ring 60 and the upper end surface of the boss portion 52 of the main bearing seat 50 may be equal to the axial length of the first diameter portion 71 of the positioning pin 70 .
  • the second diameter portion 72 and the third diameter portion 73 may be configured to have smooth surfaces, and the first mounting holes 66 and the second mounting holes 54 may be correspondingly configured to be smooth blind holes.
  • the third diameter portion 73 may be configured with an external thread, and the second mounting hole 54 may be configured as a threaded hole matched therewith, so as to further strengthen the connection between the positioning pin 70 and the main bearing seat.
  • the axial distance of the guide ring relative to the main bearing housing is determined only by the length of the first diameter portion of the stepped pin and the total length of the pin or the depth of the mounting hole Therefore, the axial position of the guide ring can be determined more accurately and simply.
  • the positioning pin 70 is configured as a stepped pin with two stepped portions in the first exemplary embodiment, the positioning pin 70 may have only one stepped portion or no stepped portion.
  • the axial position of the guide ring relative to the main bearing housing can be determined by the length of the locating pin and the depth at which the first mounting hole and the second mounting hole can accommodate the locating pin.
  • the upper end of the guide ring 60 can be axially limited by the muffler cover 24 .
  • the upper flange portion 64 of the guide ring 60 can form an interference connection or clearance fit with the muffler cover 24 , thereby keeping the guide ring 60 between the first step portion 74 of the positioning pin 70 and the muffler cover 24 between fixed positions in the axial direction.
  • the guide ring 60 further includes an outer flange portion 62 extending radially outward from the outer side wall of the ring body 1 , and the outer flange portion 62 is inserted into the housing body 26 In the gap A between the top cover 22 and the housing body 26 and the top cover 22 in the axial direction, the housing body 26 and the top cover 22 can be fixedly connected. Welded to fix.
  • the muffler cover 24 may also be formed with an outer flange portion extending outward to the gap A to be fixedly connected between the housing body 26 and the top cover 22 together with the outer flange portion 62 of the guide ring 60 , for example, it may be When welding the casing, the guide ring 60 , the muffler cover 24 , the casing body 26 and the top cover 22 are welded and fixed together, thereby further simplifying the processing process and saving processing materials.
  • the guide ring 60 Since the guide ring 60 is limited in radial and axial directions by the positioning pins 70, the guide ring 60 can be radially centered and fixed in the compressor casing at the required axial height, so the guide ring 60 can The radial centering of the fixed scroll 30 is achieved. In addition, when the fixed scroll 30 needs to be axially flexible, the guide ring 60 can also realize the axial limit of the fixed scroll 40 . Specifically, referring to FIG.
  • the inner side wall of the ring body 61 of the guide ring 60 forms a clearance fit with the outer peripheral wall 33 of the fixed scroll 30 , so as to realize the radial centering of the fixed scroll 30 and limit the radial direction of the fixed scroll 30 Moving (making the fixed scroll 30 almost impossible to move in the radial direction), in addition, the inner side wall of the ring body 61 can also serve as a guide surface to guide the axial movement of the fixed scroll 30 .
  • a third stepped portion 34 (abutting portion) is also formed on the outer peripheral wall 33 of the fixed scroll 30 , and a certain gap is formed between the lower surface of the inner flange portion 68 of the guide ring 60 and the upper surface of the third stepped portion 34 .
  • the fixed scroll 30 can move in the axial direction within a predetermined range defined by the predetermined distance. Since the axial position of the guide ring 60 is determined by the positioning pins 70 , the size of the gap between the lower surface of the inner flange portion 68 of the guide ring 60 and the upper surface of the third stepped portion 34 , that is, the fixed scroll 30 can be The range of axial movement is also indirectly determined by the locating pin 70 . That is to say, when the size of other components is determined, the size of the positioning pin 70 , especially the axial length of the first diameter section 71 , can determine the axial movement range of the fixed scroll 30 .
  • the inner side wall of the inner flange portion 68 of the guide ring 60 can also form a clearance fit with the outer peripheral wall 33 of the fixed scroll 30, so as to help realize the radial alignment of the fixed scroll 30. center and limit the radial movement of the fixed scroll 30 .
  • the fixed scroll 30 a of the scroll compressor 10 a is kept positioned in the casing by the guide ring 60 a.
  • the guide ring 60a includes a generally annular ring body 61a and a lower flange portion 68a extending axially downward from the ring body 61a.
  • the inner side wall of the ring body 61a forms a clearance fit with the outer peripheral wall 33a of the fixed scroll 30a, thereby realizing the radial centering of the fixed scroll 30a and guiding the axial movement of the fixed scroll 30a.
  • a certain gap is formed between the free end surface 65a of the lower flange portion 68a and the upper surface of the third stepped portion 34a of the outer peripheral wall 33a of the fixed scroll 30a, thereby allowing the fixed scroll 30a to move within a certain range in the axial direction.
  • the main bearing block 50a includes a base and a plurality of arms 52a (four illustrated in the figure) extending from one side of the base toward the guide ring 60a (upward), the plurality of arms 52a being circumferentially distributed on the main bearing housing 50a.
  • the arm portion 52a includes an inner side surface 56a and an upper surface 57a.
  • the inner side surface 56a of the arm portion 52a forms a clearance fit with the outer side surface 63a of the lower flange portion 68a of the guide ring 60a, thereby centering the guide ring 60a radially And restrict the radial movement of the guide ring 60a; on the other hand, the upper surface 57a of the arm portion 52a abuts the lower surface 69a of the ring body 61a of the guide ring 60a, thereby determining the axial position of the guide ring 60a.
  • the guide ring 60a is fixedly connected to the main bearing block 50a by inserting fasteners (not shown) into the mounting holes 67a of the guide ring 60a and the mounting holes 59a on the arm portion 52a of the main bearing block 50a.
  • both the guide ring 60a and the main bearing 50a have complex structures, which are not only difficult to process and install, but also consume more materials and increase the cost.
  • the guide ring 60 achieves radial centering and the determination of the axial position of the guide ring 60 through a plurality of (more than three) locating pins 70 without the need for the guide ring and the main bearing housing.
  • the structural features that match each other are processed on the top.
  • the positioning pin 70 is easier to produce and install, so the holding mechanism for the fixed scroll proposed in the present disclosure is easier to produce and assemble, saves materials and also has good reliability.
  • the present disclosure can also be produced by using existing production modules, so it has good applicability.
  • Figures 7a, 7b and 7c illustrate a positioning pin 70' according to a second exemplary embodiment of the present disclosure.
  • the main structures and functions of the scroll compressor are basically the same as those of the scroll compressor 10 of the first exemplary embodiment, and thus will not be repeated.
  • the scroll positioning pin 70 ′ is configured as a stepped pin formed by the joint assembly of the pin body 701 and the sleeve 702 sleeved on the pin body 701 .
  • the pin body 701 passes through the through hole in the sleeve 702, so that the sleeve 702 is located in the middle section of the pin body 701, thereby forming the first diameter portion 71' of the stepped pin.
  • the two sections of the pin body 701 located outside the sleeve 702 form the second diameter portion 72' and the third diameter portion 73' of the stepped pin, respectively.
  • a clearance fit or an interference fit is formed between the pin body 701 and the sleeve 702 , so that a first stepped portion 74 ′ is formed between the first diameter portion 71 ′ and the second diameter portion 72 ′, and the first diameter portion 71 ′ forms a first stepped portion 74 ′.
  • a second stepped portion 75' is formed between the third diameter portion 73'.
  • the positioning pin 70 ′ is assembled by the pin body 701 and the sleeve 702 , compared with the integrally formed stepped pin, the processing difficulty is further reduced and the processing process is simplified.
  • FIG. 8 is a partial longitudinal cross-sectional view of the scroll compressor 110 according to the third exemplary embodiment of the present disclosure.
  • the main structure and function of the scroll compressor 110 are basically the same as those of the scroll compressor 10 of the first exemplary embodiment, and thus will not be described again.
  • the holding mechanism of the scroll compressor 110 includes not only the guide ring but also the muffler cover, and the guide ring and the muffler cover are integrally formed, thereby configuring the muffler cover 160 having the function of the guide ring.
  • the muffling cover 160 includes a generally annular ring body 161 and a cover-like portion 124 located above the ring body 161 .
  • the muffling cover 160 further includes an inner flange portion 168 extending radially inward from the inner side wall of the ring body 161 and an outer flange portion 162 extending radially outward from the outer side wall of the ring body 161 .
  • the lower end of the ring body 161 of the muffler cover 160 is provided with a first mounting hole 166 for accommodating the second diameter portion 72 of the positioning pin 70 , so that the muffler cover 160 is connected to the main bearing seat 50 through the positioning pin 70 .
  • the outer flange portion 162 of the muffler cover 160 is inserted into the gap A for welding between the case body 26 and the top cover 22, so that the muffler cover 160 and the case are welded and fixed when the case is welded.
  • a clearance fit is formed between the inner side wall of the ring body 161 of the muffler cover 160 and the outer peripheral wall 33 of the fixed scroll 30, so as to realize the radial centering of the fixed scroll 30 and limit the radial movement of the fixed scroll 30,
  • the inner side wall of the ring body 161 can also serve as a guide surface to guide the axial movement of the fixed scroll 30; A certain gap is formed between them, thereby allowing the fixed scroll 30 to move within a certain range in the axial direction.
  • the cover-shaped portion 124 of the muffler cover 160 is disposed between the casing body 26 and the top cover 22 to separate the compressor internal space into the low-pressure area and the high-pressure area 12 .
  • the holding mechanism is configured as a sound-absorbing cover with a guide ring function, compared with a separate guide ring and sound-absorbing cover, the number of parts is further reduced, the installation process is simplified, and the installation accuracy is improved.
  • FIG. 9 is a partial longitudinal cross-sectional view of the scroll compressor 210 according to the fourth exemplary embodiment of the present disclosure.
  • the main structure and function of the scroll compressor 210 are basically the same as those of the scroll compressor 10 of the first exemplary embodiment, and thus will not be described again.
  • the retaining mechanism of the scroll compressor 210 includes the guide ring 260 and the muffler cover 224, wherein the guide ring 260 is no longer fixed to the housing (eg, as shown in FIG. 5, by welding the outer flange portion 62 of the guide ring 260 to housing), but is only held in its axial position by the sound-absorbing cover 224 .
  • the guide ring 260 includes a substantially annular ring body 261 and an inner flange portion 268 extending radially inward from the inner side wall of the ring body 261 .
  • a certain gap is formed between the three stepped portions 34, thereby allowing the fixed scroll 30 to move within a certain range in the axial direction.
  • the lower end of the ring body 261 of the guide ring 260 is provided with a first mounting hole 266 for accommodating the second diameter portion 72 of the positioning pin 70 , so that the guide ring 260 is connected to the main bearing seat 50 through the positioning pin 70 .
  • a fourth stepped portion 265 is formed on the upper end of the ring body 261 of the guide ring 260, and the peripheral edge portion 225 of the noise-absorbing cover 224 abuts on the fourth stepped portion 265 to form an interference connection with the guide ring 260, so that the The guide ring 260 is fixed in the axial direction.
  • the muffling cover 224 has an outer flange portion 262 extending radially outward from the outer side wall thereof, and the outer flange portion 262 is inserted into the gap A for welding between the case body 26 and the top cover 22, so that the When the housing is welded, the muffler cover 224 is welded and fixed to the housing through the outer flange portion 262 .
  • the guide ring 260 is sandwiched between the muffler cover 224 and the positioning pin 70 , specifically, between the peripheral edge portion 225 of the muffler cover 224 and the second stepped portion 74 of the positioning pin 70 , so as to be held and fixed to the housing. middle.
  • the guide ring is held and fixed in the housing only by the muffler cover and the positioning pin, it is no longer necessary to provide an outer flange portion for welding and fixing on the guide ring, thus further simplifying the processing and assembly process, reducing the difficulty of production.
  • FIG. 10 is a partial longitudinal cross-sectional view of a scroll compressor 310 according to a fourth exemplary embodiment of the present disclosure.
  • the main structure and function of the scroll compressor 310 are basically the same as those of the scroll compressor 210 of the third exemplary embodiment, and thus will not be repeated here.
  • the difference is that the guide ring 260 in the holding mechanism of the scroll compressor 310 is only used to realize the radial centering of the fixed scroll 30 , while the axial limit of the fixed scroll 30 is achieved by the muffler cover 324 .
  • the guide ring 360 is formed in a substantially annular shape.
  • the lower end of the guide ring 360 is provided with a first mounting hole 366 for accommodating the second diameter portion 72 of the positioning pin 70 , so that the guide ring 360 is connected to the main bearing seat 50 through the positioning pin 70 .
  • the upper end of the guide ring 360 is connected with the peripheral edge portion 325 of the sound-absorbing cover 324 by interference or by a fastener such as a bolt, thereby restricting the guide ring 360 in the axial direction.
  • the guide ring 360 is sandwiched between the muffler cover 324 and the positioning pin 70 , specifically, between the peripheral edge portion 325 of the muffler cover 324 and the second stepped portion 74 of the positioning pin 70 , so as to be held and fixed to the housing. middle.
  • the inner side wall of the guide ring 360 forms a clearance fit with the outer peripheral wall 33 of the fixed scroll 30, so as to realize the radial centering of the fixed scroll 30 and limit the radial movement of the fixed scroll 30 (so that the fixed scroll 30 can hardly move along the diameter of the fixed scroll 30).
  • the inner side wall of the guide ring 360 can also serve as a guide surface to guide the axial movement of the fixed scroll 30 .
  • the muffling cover 324 includes an outer flange portion 362 extending radially outward from its outer side wall and an inner flange portion 368 extending radially inward from its inner side wall.
  • the outer flange portion 362 is inserted into the gap A for welding between the casing body 26 and the top cover 22 , so that the muffler cover 324 is welded and fixed to the casing through the outer flange portion 362 when the casing is welded.
  • a certain gap is formed between the inner flange portion 368 and the third stepped portion 34 of the outer peripheral wall 33 of the fixed scroll 30, thereby allowing the fixed scroll 30 to move within a certain range in the axial direction.
  • the guide ring is only kept and fixed in the housing by the muffler cover and the positioning pin, the processing and assembling process are further simplified, and the production difficulty is reduced.
  • the guide ring since the guide ring only has a simple annular structure, the existing production modules can be directly used, and the applicability is better and the production cost is lower.

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  • General Engineering & Computer Science (AREA)
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Abstract

一种涡旋压缩机，该涡旋压缩机包括：壳体（20）、涡旋机构和主轴承座（50），该涡旋机构包括定涡旋（30），定涡旋（30）包括端板（31）、从端板（31）延伸的涡卷（32）和外周壁（33），外周壁（33）设置在涡卷（32）的外周，主轴承座（50）支撑涡旋机构，其中，涡旋压缩机还包括保持机构和定位销（70,70'），保持机构围绕外周壁（33）布置以限制定涡旋（30）的径向运动，定位销（70,70'）连接至保持机构的第一安装孔（66）和主轴承座（50）的第二安装孔（54）并且在轴向上布置在保持机构与主轴承座（50）之间，从而确定保持机构相对于主轴承座（50）的轴向位置。该涡旋压缩机的保持机构与主轴承座的加工更加简单、用料更加节省，并且保持机构与主轴承座的安装难度更低。

Description

涡旋压缩机
本申请要求以下中国专利申请的优先权：于2020年9月21日提交中国专利局的申请号为202010997708.4、发明创造名称为“涡旋压缩机”的中国专利申请；于2020年9月21日提交中国专利局的申请号为202022080759.9、发明创造名称为“涡旋压缩机”的中国专利申请。这些专利申请的全部内容通过引用结合在本申请中。
技术领域
本公开涉及一种涡旋压缩机，更具体地，涉及一种定涡旋的保持机构。
背景技术
涡旋压缩机一般包括壳体、容纳在壳体中的驱动机构、由驱动机构驱动的涡旋机构、支撑涡旋机构的主轴承座等。涡旋机构一般包括相互啮合的动涡旋和定涡旋。定涡旋通过保持机构定位在压缩机中。一方面，保持机构需要在径向上限制定涡旋的移动并且使定涡旋的径向对中；另一方面，保持机构能够允许定涡旋沿轴向在一定范围内轴向运动，从而为涡旋压缩机提供一定的轴向柔性。
现有技术中常用的一种定涡旋的保持方式是：在定涡旋的外周设置有凸耳，在凸耳中形成有通孔，在主轴承座的臂部中形成有螺纹孔，通过带有导向套管的螺栓将定涡旋和主轴承座固定在一起，从而实现定涡旋的径向对中。由于定涡旋的凸耳中所形成的通孔能够沿着导向套管在轴向上滑动，因此允许定涡旋相对于主轴承座轻微地轴向运动。
现有技术中常用的另一种定涡旋的保持方式是：在定涡旋的外周设置一个导向环，导向环中设置有通孔，使用螺栓穿过导向环中的通孔且旋拧在主轴承座的螺纹孔中。导向环能够对定涡旋进行径向限位并允许定涡旋沿轴向在一定范围内运动。
然而，以上两种定涡旋的保持方式中，第一种保持方式需要在定涡旋上加工凸耳及通孔并且配合使用导向套管和螺栓，这会增加定涡旋的径向尺寸并增加组装成本和组装时间。第二种保持方式需要在导向环上加工出与固定构件(例 如主轴承座)相匹配的结构特征才能实现导向环的径向对中，这也会增加压缩机的加工难度和加工成本。因此，存在改进定涡旋部件的保持方式的需求。
发明内容
本公开的目的在于提供一种具有新的定涡旋的保持机构的涡旋压缩机，该涡旋压缩机不仅能够实现定涡旋的径向限位、允许定涡旋相对于主轴承座在一定范围内轴向运动，而加工简便、安装容易、用料节省。
根据本公开的一个方面，提供了一种涡旋压缩机，该涡旋压缩机包括：壳体、涡旋机构和主轴承座，该涡旋机构包括定涡旋，定涡旋包括端板、从端板延伸的涡卷和外周壁，外周壁设置在涡卷的外周，主轴承座支撑涡旋机构，其中，涡旋压缩机还包括保持机构和定位销，保持机构围绕外周壁布置以限制定涡旋的径向运动，定位销连接至保持机构的第一安装孔和主轴承座的第二安装孔并且在轴向上布置在保持机构与主轴承座之间，从而确定保持机构相对于主轴承座的轴向位置。
可选地，保持机构包括导向环，导向环与外周壁径向间隙配合以引导定涡旋的轴向运动。
可选地，保持机构还包括将涡旋压缩机的内部空间分隔为低压区和高压区的消音盖，导向环与消音盖分体形成。
可选地，消音盖与导向环过盈连接或通过紧固件连接，从而将导向环固定在定位销与消音盖之间。
可选地，消音盖与导向环间隙配合，导向环和/或消音盖包括沿径向向外延伸的外凸缘部，外凸缘部固定地连接至壳体。
可选地，壳体包括壳体本体和顶盖，并且：导向环的外凸缘部在轴向上固定地连接在壳体本体与顶盖之间；或者导向环的外凸缘部与消音盖的外凸缘部一起在轴向上固定地连接在壳体本体与顶盖之间。
可选地，导向环或消音盖包括沿径向向内延伸的内凸缘部，定涡旋处形成有抵接部，内凸缘部与抵接部之间在轴向上存在预定距离，从而使得定涡旋能够在由预定距离限定的范围内轴向运动。
可选地，保持机构还包括将涡旋压缩机的内部空间分隔为低压区和高压区的消音盖，保持机构由导向环与消音盖一体形成，保持机构包括沿径向向外 延伸的的外凸缘部和沿径向向内延伸的内凸缘部，外凸缘部固定地连接至壳体，内凸缘部与定涡旋的抵接部在轴向上存在预定距离，从而使得定涡旋能够在由预定距离限定的范围内轴向运动。
可选地，壳体包括壳体本体和顶盖，并且保持机构的外凸缘部在轴向上固定地连接在壳体本体与顶盖之间。
可选地，定位销为沿周向分布的至少三个定位销。
可选地，定位销构造为具有第一台阶部和/或第二台阶部的台阶销，第一台阶部与保持机构的设置有第一安装孔的端面抵接，第二台阶部与主轴承座的设置有第二安装孔的端面抵接。
可选地，台阶销为一体成形的一体式销，或者台阶销为包括销体和套设在销体上的套管的分体式销。
根据本公开的涡旋压缩机，其定涡旋通过保持机构实现径向对中和轴向柔性，而保持机构则通过定位销连接至主轴承座并实现其径向对中以及轴向定位，从而避免了保持机构与主轴承座直接配合而导致的对保持机构和主轴承座的配合部位的加工，节省了用料、降低了加工及安装难度；保持机构可以一体形成，从而简化安装过程。
附图说明
通过以下参照附图的描述，本公开的一个或多个实施方式的特征和优点将变得更加容易理解。这里所描述的附图仅是出于说明目的而并非意图以任何方式限制本公开的范围。附图并非按比例绘制，而是可以放大或缩小一些特征以显示特定部件的细节。在附图中：
图1是根据本公开的第一示例性实施方式的涡旋压缩机的局部纵剖面图；
图2是根据本公开的第一示例性实施方式的涡旋压缩机的一部分的立体示意图；
图3是根据本公开的第一示例性实施方式的涡旋压缩机的示出了涡旋机构的横截面的剖视图；
图4是根据本公开的第一示例性实施方式的涡旋压缩机的一部分的立体分解图；
图5是根据本公开的第一示例性实施方式的涡旋压缩机的局部细节纵剖视 图，其中示出了涡旋压缩机的保持机构；
图6是根据本公开的第一示例性实施方式的台阶销的立体示意图；
图7a、图7b和图7c分别示出了根据本公开的第二示例性实施方式的台阶销及其组成部件的立体示意图；
图8是根据本公开的第三示例性实施方式的涡旋压缩机的局部纵剖面图；
图9是根据本公开的第四示例性实施方式的涡旋压缩机的局部纵剖面图；
图10是根据本公开的第五示例性实施方式的涡旋压缩机的局部纵剖面图；
图11是根据本公开的对比示例的涡旋压缩机的局部纵剖面图；以及
图12和图13分别是根据本公开的对比示例的涡旋压缩机的主轴承座及导向环的立体示意图。
具体实施方式
下面将参照附图对本公开的优选实施方式进行描述，该描述仅仅是示例性的，而不构成对本公开及其应用的限制。
图1是根据本公开的第一示例性实施方式的涡旋压缩机的局部纵剖面图。如图1所示，涡旋压缩机10主要包括壳体20、涡旋机构、主轴承座50以及驱动机构(未示出)。壳体20通常包括呈大致圆筒形的壳体本体26、顶盖22以及底盖(未示出)，壳体本体26、顶盖(顶盖)22以及底盖通过例如焊接形成完整的壳体20。涡旋压缩机20还设置有位于壳体本体26与顶盖22之间的消音盖24，从而将压缩机内部空间分隔为低压区14和高压区12。工作流体经由设置壳体本体26上的吸气口配件29进入低压区12，经由涡旋机构压缩后进入高压区12并通过设置在顶盖22的排气口配件28排出到涡旋压缩机10外。涡旋机构包括定涡旋30和动涡旋40。涡旋机构由驱动机构驱动。具体地，当驱动机构的驱动轴旋转时，能够经由驱动轴的曲柄销驱动动涡旋40，并且由于与动涡旋40和定涡旋30联接的十字滑环80，动涡旋40能够相对于定涡旋30进行平动转动。换句话说，动涡旋40的轴线相对于定涡旋30的轴线沿圆形轨道绕动，但是动涡旋40和定涡旋30二者本身不会绕它们各自的轴线旋转。涡旋机构由主轴承座50支承，主轴承座50通过比如铆接等方式与壳体本体26固定连接或者与壳体本体26一体地形成。
定涡旋30包括端板31和从端板31的一侧向下延伸的螺旋形的涡卷32。 定涡旋30的涡卷32与动涡旋40的涡卷42彼此啮合，因此在它们之间形成一系列的用于压缩流体例如制冷剂的压缩腔。定涡旋30还包括从端板31向下延伸并且设置在定涡旋30的涡卷32外周的大致圆筒形的外周壁33。定涡旋30通过保持机构定位在涡旋压缩机10中。保持机构可以包括导向环60。参见图2和图3，导向环60围绕定涡旋30的外周壁33布置，导向环60的下端通过定位销70连接至主轴承座50，导向环60的上端通过消音盖24限位。主轴承座50包括基部和从基部的一侧朝向导向环60(向上)延伸的三个凸台部52，三个凸台部52沿周向分布在主轴承座50上。定位销70在轴向上设置在导向环30与主轴承座50的凸台部52之间，一端固定在凸台部52中，另一端与导向环60连接，从而确定导向环60相对于主轴承座50的轴向位置。本领域技术人员可以理解的是，凸台部52与定位销70的数量不限于图中所示的三个，也可以多于三个。
下面参照图4和图5对包括有导向环60进行详细描述。如图4和图5所示，导向环60包括大致环形的环本体61、从环本体61的内侧壁沿径向向内延伸的内凸缘部68以及从环本体61的上端面沿轴向向上延伸的上凸缘部64。导向环60还在环本体61的下端面的与定位销70相对应的位置处设置有第一安装孔66。主轴承座50的凸台部52中形成有用于接纳定位销70的第二安装孔54，第二安装孔54与第一安装孔66在轴向上对准，定位销70的一端***导向环60的第一安装孔66中，另一端***主轴承座50的第二安装孔54中，从而将导向环60连接至主轴承座50。由于主轴承座50的凸台部52及其第二安装孔54沿周向分布，因此通过定位销70定位的导向环60能够实现径向对中的安装。本领域技术人员可以理解的是，主轴承座50也可以不包括凸台部52，而是将定位销70直接连接至主轴承座50。
参见图6，定位销70构造为具有台阶部74的台阶销。定位销70包括第一直径部71、第二直径部72和第三直径部73，第二直径部72与第三直径部73的直径均小于第一直径部71的直径。第二直径部72与第三直径部73分别形成在定位销70的两端，而第一直径部72形成在定位销70的中段，从而在第二直径部72与第一直径部71的连接处以及第三直径部73与第一直径部71的连接处分别形成第一台阶部74和第二台阶部75。参见图5，第二直径部72与导向环60的第一安装孔66匹配，第三直径部73与主轴承座60的第二安装孔54 匹配，使得当定位销70两端的第二直径部72和第三直径部73分别***在轴向上对准的第一安装孔66和第二安装孔54中时，第一台阶部74与导向环60的环本体61的设置有第一安装孔66的下端面相抵接，第二台阶部75与主轴承座50的凸台部52的设置有第二安装孔54的上端面相抵接，由此导向环60相对于主轴承座50的轴向位置被定位销70确定。导向环60的环本体61的下端面与主轴承座50的凸台部52的上端面之间的轴向距离可以等于定位销70的第一直径部71的轴向长度。第二直径部72和第三直径部73可以构造为具有光滑的表面，并且第一安装孔66和第二安装孔54可以相应地构造为光滑的盲孔。优选地，第三直径部73可以构造为带有外螺纹，并且第二安装孔54构造为与其匹配的螺纹孔，从而进一步加强定位销70与主轴承座的连接。
通过将定位销构造为具有两个台阶部的台阶销，使得导向环相对于主轴承座的轴向距离仅取决于台阶销的第一直径部的长度而与销的总长度或安装孔的深度无关，从而能够更加准确、更加简单地确定导向环的轴向位置。
另外。本领域技术人员可以理解的是，虽然在第一示例性实施方式中定位销70构造为具有两个台阶部的台阶销，但是定位销70也可以仅具有一个台阶部或者不具有台阶部。在这种情况下，导向环相对于主轴承座的轴向位置可以通过定位销的长度以及第一安装孔和第二安装孔能够容纳定位销的深度来确定。
导向环60的上端可以通过消音盖24进行轴向限位。具体地，参见图5，导向环60的上凸缘部64能够与消音盖24形成过盈连接或间隙配合，从而将导向环60保持在定位销70的第一台阶部74与消音盖24之间的在轴向上固定的位置处。为了使导向环60更加稳定可靠地固定在壳体中，导向环60还包括从环本体1的外侧壁沿径向向外延伸的外凸缘部62，外凸缘部62***壳体本体26与顶盖22之间的间隙A中以在轴向上固定地连接在壳体本体26与顶盖22之间，例如可以在焊接壳体时将导向环60通过外凸缘部62与壳体焊接固定。另外，消音盖24也可以形成有向外延伸至间隙A的外凸缘部以与导向环60的外凸缘部62一起固定地连接在在壳体本体26与顶盖22之间，例如可以在焊接壳体时将导向环60、消音盖24、壳体本体26和顶盖22一起焊接固定，从而进一步简化加工过程、节省加工用料。
由于导向环60通过定位销70实现了径向和轴向的限位，使得导向环60 能够径向对中地且以所需要的轴向高度固定在压缩机壳体中，因此导向环60能够实现定涡旋30的径向对中。另外，在定涡旋30需要具有轴向柔性的情况下，导向环60还能够实现定涡旋40的轴向限位。具体地，参见图5，导向环60的环本体61的内侧壁与定涡旋30的外周壁33形成间隙配合，从而实现定涡旋30的径向对中并限制定涡旋30的径向移动(使定涡旋30几乎不能沿径向移动)，另外环本体61的内侧壁还能够作为引导表面引导定涡旋30的轴向移动。定涡旋30的外周壁33上还形成有第三台阶部34(抵接部)，导向环60的内凸缘部68的下表面与该第三台阶部34的上表面之间形成有一定的间隙(在轴向上的预定距离)，从而允许定涡旋30沿轴向在由该预定距离限定的预定范围内移动。由于导向环60的轴向位置由定位销70确定，因此导向环60的内凸缘部68的下表面与该第三台阶部34的上表面之间的间隙的大小、即定涡旋30能够轴向移动的范围也由定位销70间接地确定。也就是说，在其他部件的尺寸确定的情况下，确定定位销70的尺寸、尤其是第一直径段71的轴向长度，即可以确定定涡旋30的轴向运动范围。另外，本领域技术人员还可以理解的是，导向环60的内凸缘部68的内侧壁也可以与定涡旋30的外周壁33形成间隙配合，从而帮助实现定涡旋30的径向对中并限制定涡旋30的径向移动。
下面将参照图11至图13中所示出的对比示例中的涡旋压缩机10a对本公开的效果进行描述。如图11、图12、图13所示，在对比示例中，涡旋压缩机10a的定涡旋30a通过导向环60a保持定位在壳体中。导向环60a包括大致环形的环本体61a和从环本体61a沿轴向向下延伸的下凸缘部68a。环本体61a的内侧壁与定涡旋30a的外周壁33a形成间隙配合，从而实现定涡旋30a的径向对中并引导定涡旋30a的轴向移动。下凸缘部68a的自由端面65a与定涡旋30a的外周壁33a的第三台阶部34a的上表面之间形成有一定的间隙，从而允许定涡旋30a沿轴向在一定范围内移动。
导向环60a的径向对中和轴向限位通过与主轴承座50a配合而实现。具体地，参见图12，主轴承座50a包括基部和从基部的一侧朝向导向环60a(向上)延伸的多个臂部52a(在图中示例为四个)，多个臂部52a沿周向分布在主轴承座50a上。臂部52a包括内侧表面56a和上表面57a。当导向环60a安装在主轴承座50a中时，一方面，臂部52a的内侧表面56a与导向环60a的下凸缘部68a的外侧表面63a形成间隙配合，从而使得导向环60a径向对中并限制导向环60a 的径向移动；另一方面，臂部52a的上表面57a与导向环60a的环本体61a的下表面69a抵接，从而确定导向环60a的轴向位置。最后，通过将紧固件(未示出)***到导向环60a的安装孔67a和主轴承座50a的臂部52a上的安装孔59a中而将导向环60a与主轴承座50a固定连接。
在该对比示例中，为了实现导向环60a的径向对中和轴向限位，需要在导向环60a和主轴承座50a上分别加工出相互匹配的结构特征，例如包括内侧表面56a、上表面57a和安装孔59a的臂部52a以及包括外侧表面63a的下凸缘部68a等。因此，无论是导向环60a还是主轴承50a的结构都较为复杂，不仅难以加工和安装，而且消耗更多的物料、导致成本上升。相比之下，在本公开中，导向环60通过多个(三个以上)定位销70实现径向对中并实现导向环60的轴向位置的确定，而无需在导向环和主轴承座上加工相互匹配的结构特征。定位销70作为一种通用零件，更加容易生产和安装，因此本公开所提出的用于定涡旋的保持机构更容易生产组装、用料更加节省并且同样具有良好的可靠性。另外，本公开还能够采用现有的生产模块进行生产，因此具有良好适用性。
图7a、图7b和图7c示出了根据本公开的第二示例性实施方式的定位销70'。在本公开的第二示例性实施方式中，涡旋压缩机与第一示例性实施方式的涡旋压缩机10的主要结构和功能基本一致，因此不再赘述。区别在于，涡旋定位销70'构造为由销体701和套设在销体701上的套管702共同组装形成的台阶销。具体地，销体701穿过套管702中的通孔，使得套管702位于销体701的中段，从而形成台阶销的第一直径部71'。销体701的位于套管702外的两个部段分别形成台阶销的第二直径部72'和第三直径部73'。销体701与套管702之间形成间隙配合或过盈配合，从而在第一直径部71'与第二直径部72'之间形成第一台阶部74'，并且在第一直径部71'与第三直径部73'之间形成第二台阶部75'。
根据第二示例性实施方式，由于定位销70'通过销体701和套管702组装而成，相较于一体形成的台阶销，进一步降低了加工难度、简化了加工过程。
图8是根据本公开的第三示例性实施方式的涡旋压缩机110的局部纵剖面图。该涡旋压缩机110与第一示例性实施方式的涡旋压缩机10的主要结构和功能基本一致，因此不再赘述。区别在于，涡旋压缩机110的保持机构不仅包括导向环，而且还包括消音盖，并且导向环和消音盖一体形成，从而构造为具有 导向环功能的消音盖160。消音盖160包括大致环形的环本体161和位于环本体161上方的盖状部124。消音盖160还包括从环本体161的内侧壁沿径向向内延伸的内凸缘部168以及从环本体161的外侧壁沿径向向外延伸的外凸缘部162。消音盖160的环本体161的下端设置有用于容纳定位销70的第二直径部72的第一安装孔166，从而使得消音盖160通过定位销70连接至主轴承座50。消音盖160的外凸缘部162***壳体本体26与顶盖22之间的用于焊接的间隙A中，从而在焊接壳体时将消音盖160与壳体焊接固定。一方面，消音盖160的环本体161的内侧壁与定涡旋30的外周壁33之间形成间隙配合，从而实现定涡旋30的径向对中并限制定涡旋30的径向移动，环本体161的内侧壁还能够作为引导表面引导定涡旋30的轴向移动；另一方面，消音盖160的内凸缘部168与定涡旋30的外周壁33的第三台阶部34之间形成一定的间隙，从而允许定涡旋30沿轴向在一定范围内移动。另外，消音盖160的盖状部124设置在壳体本体26与顶盖22之间，以将压缩机内部空间分隔为低压区和高压区12。
根据第三示例性实施方式，由于保持机构构造为具有导向环功能的消音盖，相较于分体的导向环和消音盖，进一步减少了零件数量、简化了安装过程、提高了安装精度。
图9是根据本公开的第四示例性实施方式的涡旋压缩机210的局部纵剖面图。该涡旋压缩机210与第一示例性实施方式的涡旋压缩机10的主要结构和功能基本一致，因此不再赘述。区别在于，涡旋压缩机210的保持机构包括导向环260和消音盖224，其中的导向环260不再固定至壳体(例如图5所示的通过导向环260的外凸缘部62焊接至壳体)，而是仅通过消音盖224固定在其轴向位置中。具体地，导向环260包括大致环形的环本体261和从环本体261的内侧壁沿径向向内延伸的内凸缘部268，内凸缘部268与定涡旋30的外周壁33的第三台阶部34之间形成一定的间隙，从而允许定涡旋30沿轴向在一定范围内移动。一方面，导向环260的环本体261的下端设置有用于容纳定位销70的第二直径部72的第一安装孔266，从而使得导向环260通过定位销70连接至主轴承座50。另一方面，导向环260的环本体261的上端形成有第四台阶部265，消音盖224的周缘部225抵接在该第四台阶部265上，与导向环260形成过盈连接，从而在轴向上对导向环260进行固定。另外，消音盖224具有从其外侧壁沿径向向外延伸的外凸缘部262，外凸缘部262***壳体本体26与顶盖 22之间的用于焊接的间隙A中，从而在焊接壳体时将消音盖224通过外凸缘部262与壳体焊接固定。由此，导向环260被夹持在消音盖224与定位销70之间、具体地在消音盖224的周缘部225与定位销70的第二台阶部74之间，从而被保持固定在壳体中。
根据第四示例性实施方式，由于导向环仅通过消音盖与定位销保持固定在壳体中，不再需要在导向环上设置用于焊接固定的外凸缘部，因此进一步简化了加工及组装过程、降低了生产难度。
图10是根据本公开的第四示例性实施方式的涡旋压缩机310的局部纵剖面图。该涡旋压缩机310与第三示例性实施方式的涡旋压缩机210的主要结构和功能基本一致，因此不再赘述。区别在于，涡旋压缩机310的保持机构中的导向环260仅用于实现定涡旋30的径向对中，而定涡旋30的轴向限位则通过消音盖324实现。具体地，导向环360形成为大致环形。导向环360的下端设置有用于容纳定位销70的第二直径部72的第一安装孔366，从而使得导向环360通过定位销70连接至主轴承座50。导向环360的上端与消音盖324的周缘部325过盈连接或者通过例如螺栓的紧固件连接，从而在轴向上对导向环360进行限制。由此，导向环360被夹持在消音盖324与定位销70之间、具体地在消音盖324的周缘部325与定位销70的第二台阶部74之间，从而被保持固定在壳体中。导向环360的内侧壁与定涡旋30的外周壁33形成间隙配合，从而实现定涡旋30的径向对中并限制定涡旋30的径向移动(使定涡旋30几乎不能沿径向移动)，另外导向环360的内侧壁还能够作为引导表面引导定涡旋30的轴向移动。
消音盖324包括从其外侧壁沿径向向外延伸的外凸缘部362和从其内侧壁沿径向向内延伸的内凸缘部368。外凸缘部362***壳体本体26与顶盖22之间的用于焊接的间隙A中，从而在焊接壳体时将消音盖324通过外凸缘部362与壳体焊接固定。内凸缘部368与定涡旋30的外周壁33的第三台阶部34之间形成一定的间隙，从而允许定涡旋30沿轴向在一定范围内移动。
在第五示例性实施方式中，与第四示例性实施方式类似，由于导向环仅通过消音盖与定位销保持固定在壳体中，因此进一步简化了加工及组装过程、降低了生产难度。另外，由于导向环仅具有简单的环形结构，能够直接利用已有的生产模块，适用性更好、生产成本更加低廉。
本领域技术人员可以理解的是，本公开允许多种轴向限定方式来控制导向环的轴向位置并将导向环固定在壳体中，而不限于本公开的示例性实施方式中描述的具体方式。
尽管在此已详细描述本公开的各种实施方式，但是应该理解本公开并不局限于这里详细描述和示出的具体实施方式，在不偏离本公开的实质和范围的情况下可由本领域的技术人员实现其它的变型和变体。所有这些变型和变体都落入本公开的范围内。而且，所有在此描述的构件都可以由其他技术性上等同的构件来代替。

Claims (12)

  1. 一种涡旋压缩机(10，110，210，310)，所述涡旋压缩机(10，110，210，310)包括：
    壳体(20)；
    涡旋机构，所述涡旋机构包括定涡旋(30)，所述定涡旋(30)包括：端板(31)，从所述端板(31)延伸的涡卷(32)和外周壁(33)，所述外周壁(33)设置在所述涡卷(32)的外周；以及
    主轴承座(50)，所述主轴承座(50)支撑所述涡旋机构；
    其特征在于，所述涡旋压缩机还包括保持机构和定位销(70，70')，所述保持机构围绕所述外周壁(33)布置以限制所述定涡旋(30)的径向运动，所述定位销(70，70')连接至所述保持机构的第一安装孔(66，166，266，366)和所述主轴承座(50)的第二安装孔(54)并且在轴向上布置在所述保持机构与所述主轴承座(50)之间，从而确定所述保持机构相对于所述主轴承座(50)的轴向位置。
  2. 根据权利要求1所述的涡旋压缩机(10，110，210，310)，其特征在于，所述保持机构包括导向环(60，260，360)，所述导向环(60，260，360)与所述外周壁(33)径向间隙配合以引导所述定涡旋(30)的轴向运动。
  3. 根据权利要求2所述的涡旋压缩机(10，110，210，310)，其特征在于，所述保持机构还包括将所述涡旋压缩机的内部空间分隔为低压区和高压区的消音盖(24，224，324)，所述导向环与所述消音盖分体形成。
  4. 根据权利要求3所述的涡旋压缩机(10，110，210，310)，其特征在于，所述消音盖与所述导向环过盈连接或通过紧固件连接，从而将所述导向环固定在所述定位销与所述消音盖之间。
  5. 根据权利要求3所述的涡旋压缩机(10，110，210，310)，其特征在于，所述消音盖与所述导向环间隙配合，所述导向环和/或所述消音盖包括沿 径向向外延伸的外凸缘部(62，262，362)，所述外凸缘部固定地连接至所述壳体(20)。
  6. 根据权利要求5所述的涡旋压缩机(10，110，210，310)，其特征在于，所述壳体包括壳体本体(26)和顶盖(22)，并且：
    所述导向环的外凸缘部在轴向上固定地连接在所述壳体本体(26)与所述顶盖(22)之间；或者
    所述导向环的外凸缘部与所述消音盖的外凸缘部一起在轴向上固定地连接在所述壳体本体(26)与所述顶盖(22)之间。
  7. 根据权利要求3所述的涡旋压缩机(10，110，210，310)，其特征在于，所述导向环或所述消音盖包括沿径向向内延伸的内凸缘部(68，268，368)，所述定涡旋(30)处形成有抵接部(34)，所述内凸缘部(68，268，368)与所述抵接部(34)之间在轴向上存在预定距离，从而使得所述定涡旋能够在由所述预定距离限定的范围内轴向运动。
  8. 根据权利要求2所述的涡旋压缩机(10，110，210，310)，其特征在于，所述保持机构还包括将所述涡旋压缩机的内部空间分隔为低压区和高压区的消音盖(160)，所述保持机构由所述导向环与所述消音盖一体形成，所述保持机构包括沿径向向外延伸的外凸缘部(162)和沿径向向内延伸的内凸缘部(168)，所述外凸缘部固定地连接至所述壳体(20)，所述内凸缘部与所述定涡旋(30)的抵接部(34)在轴向上存在预定距离，从而使得所述定涡旋能够在由所述预定距离限定的范围内轴向运动。
  9. 根据权利要求8所述的涡旋压缩机(10，110，210，310)，其特征在于，所述壳体包括壳体本体(26)和顶盖(22)，并且所述保持机构的外凸缘部(162)在轴向上固定地连接在所述壳体本体(26)与所述顶盖(22)之间。
  10. 根据权利要求1-9中任一项所述的涡旋压缩机(10，110，210，310)，其特征在于，所述定位销(70，70')为沿周向分布的至少三个定位销。
  11. 根据权利要求1-9中任一项所述的涡旋压缩机(10，110，210，310)，其特征在于，所述定位销(70，70')构造为具有第一台阶部(74，74')和/或第二台阶部(75，75')的台阶销，所述第一台阶部(74，74')与所述保持机构的设置有所述第一安装孔(66，166，266，366)的端面抵接，所述第二台阶部(75，75')与所述主轴承座(20)的设置有所述第二安装孔(54)的端面抵接。
  12. 根据权利要求11所述的涡旋压缩机(10，110，210，310)，其特征在于，所述台阶销(70)为一体成形的一体式销，或者所述台阶销(70')为包括销体(701)和套设在所述销体(701)上的套管(702)的分体式销。
PCT/CN2020/128536 2020-09-21 2020-11-13 涡旋压缩机 WO2022057063A1 (zh)

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JPH09264271A (ja) * 1996-03-27 1997-10-07 Mitsubishi Electric Corp スクロール圧縮機の製造方法
JP2002039083A (ja) * 2000-07-27 2002-02-06 Mitsubishi Heavy Ind Ltd スクロール型流体機械
CN1932246A (zh) * 2005-09-12 2007-03-21 科普兰公司 带法兰的套筒导向件
WO2010016692A2 (ko) * 2008-08-05 2010-02-11 두원공과대학교 스크롤 유체기계
CN201443511U (zh) * 2009-07-15 2010-04-28 大连三洋压缩机有限公司 一种涡旋式制冷压缩机
CN102748294A (zh) * 2012-08-07 2012-10-24 苏州英华特制冷设备技术有限公司 一种涡旋压缩机的径向防自转机构
CN103225610A (zh) * 2007-09-11 2013-07-31 艾默生环境优化技术有限公司 带有保持机构的压缩机
CN110486274A (zh) * 2019-09-09 2019-11-22 苏州旭星涡旋压缩机有限公司 一种用于涡旋压缩机的径向防自转机构
CN209781209U (zh) * 2019-04-26 2019-12-13 艾默生环境优化技术(苏州)有限公司 涡旋压缩机

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09264271A (ja) * 1996-03-27 1997-10-07 Mitsubishi Electric Corp スクロール圧縮機の製造方法
JP2002039083A (ja) * 2000-07-27 2002-02-06 Mitsubishi Heavy Ind Ltd スクロール型流体機械
CN1932246A (zh) * 2005-09-12 2007-03-21 科普兰公司 带法兰的套筒导向件
CN103225610A (zh) * 2007-09-11 2013-07-31 艾默生环境优化技术有限公司 带有保持机构的压缩机
WO2010016692A2 (ko) * 2008-08-05 2010-02-11 두원공과대학교 스크롤 유체기계
CN201443511U (zh) * 2009-07-15 2010-04-28 大连三洋压缩机有限公司 一种涡旋式制冷压缩机
CN102748294A (zh) * 2012-08-07 2012-10-24 苏州英华特制冷设备技术有限公司 一种涡旋压缩机的径向防自转机构
CN209781209U (zh) * 2019-04-26 2019-12-13 艾默生环境优化技术(苏州)有限公司 涡旋压缩机
CN110486274A (zh) * 2019-09-09 2019-11-22 苏州旭星涡旋压缩机有限公司 一种用于涡旋压缩机的径向防自转机构

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