CN103821718A - Variable speed scroll compressor - Google Patents
Variable speed scroll compressor Download PDFInfo
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- CN103821718A CN103821718A CN201310581293.2A CN201310581293A CN103821718A CN 103821718 A CN103821718 A CN 103821718A CN 201310581293 A CN201310581293 A CN 201310581293A CN 103821718 A CN103821718 A CN 103821718A
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- rotor
- variable speed
- live axle
- scroll compressor
- stator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
- F04C29/045—Heating; Cooling; Heat insulation of the electric motor in hermetic pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- F04C18/0207—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 both members having co-operating elements in spiral form
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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
- F04C18/0207—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 both members having co-operating elements in spiral form
- F04C18/0215—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 both members having co-operating elements in spiral form where only one member is moving
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/0078—Fixing rotors on shafts, e.g. by clamping together hub and shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/40—Electric motor
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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
The present invention discloses a variable speed scroll compressor (2) including a closed casing (3) including a low pressure volume and a high pressure volume, and an electric motor arranged in the low pressure volume and including a rotor (21) and a stator (22), the rotor (21) including permanent magnets, the stator (22) including a stator core (26) provided with a plurality of radially extending tooth portions (28) and with a plurality of slots formed between the radially extending tooth portions (28), and stator windings (27). Each stator winding (27) is wound around a respective tooth portion (28) and includes winding portions extending respectively in the slots formed on each side of the respective tooth portion (28).
Description
Technical field
The present invention relates to a kind of variable speed scroll compressor.
Background technique
Known scroll compressor can comprise:
-comprise the closure of low pressure volume and high pressure volume, and
-be arranged in the speed-variable motor in low pressure volume.This motor comprises rotor and stator.Rotor comprises permanent magnet, and described stator comprises stator core body and staor winding.Stator core body is provided with multiple toothed region of radially extending and is formed on the multiple grooves between multiple toothed region of radially extending.Multiple staor winding are in multiple toothed region of radially extending.
In this scroll compressor, staor winding has almost filled up the groove being arranged in stator core body completely.Therefore,, in the time of work, enter the low-temperature low-pressure refrigerant of low pressure volume substantially by the circlet shape gap circulation of defining between rotor core body and stator core body.
As a result, staor winding is likely inadequate with the cooling of permanent magnet being arranged in rotor core body.This can cause the demagnetization (because hot staor winding causes the superheating of permanent magnet) of permanent magnet.Slow-speed of revolution situation when this problem is low for refrigerant flow is particularly serious.
In addition, due to the circlet shape gap circulation of refrigeration agent by defining between rotor core body and stator core body, the pressure drop of refrigeration agent is higher, and this low compression efficiency that especially can the high speed conditions in the time that refrigerant flow is high declines.
Summary of the invention
The object of the invention is to propose a kind of improved variable speed scroll compressor, it can overcome the problem that traditional scroll compressor runs into.
Another object of the present invention is to provide a kind of reliable and variable speed scroll compressor that efficiency improves.
This variable speed scroll compressor according to the present invention comprises:
-comprise the closure of low pressure volume and high pressure volume;
-be suitable for the compression unit of compressed refrigerant;
-be arranged in described low pressure volume and comprise the motor of rotor and stator, described rotor comprises permanent magnet, described stator comprises stator core body and staor winding, described stator core body be provided with multiple radially extend toothed region and multiple being formed on described in radially extend toothed region between groove, described staor winding is in described toothed region of radially extending, and each staor winding is in the toothed region of each correspondence;
-being suitable for the live axle of drive compression unit, described live axle is connected to described rotor rotationally, and
-be arranged on the described epitrochanterian first axial abutment surface and be arranged on the axial abutment surface of second on described live axle, between the described first and second axial abutment surfaces, leave predetermined axial clearance, in order to allow that limited sliding movement to axial occurs between described rotor and described live axle
Wherein, at least one groove forming between the first and second adjacent toothed region of radially extending comprises the first slot part, the second slot part and the 3rd slot part, extends in described the first slot part around the winding part of the described first toothed region of radially extending the first staor winding around; Winding part around the described second toothed region of radially extending the second staor winding is around extended in described the second slot part; Described the 3rd slot part is between described the first slot part and described the second slot part, and it defines refrigerant flow path.
The winding of staor winding in the toothed region of stator core body allows the free-flow cross section that keeps large in the groove of stator for making flow of refrigerant pass through the groove of described stator.This makes the pressure drop of refrigeration agent be reduced and promote thus compression efficiency on the one hand, has improved on the other hand cooling (even in the slow-revving situation of motor) of staor winding.
Therefore, no matter compressor according to the present invention is under which kind of operating conditions, stator core body and rotor core body, and especially permanent magnet can be protected effectively in order to avoid any degeneration.
According to one embodiment of the invention, the each groove being formed between the first and second adjacent toothed region of radially extending comprises the first slot part, the second slot part and the 3rd slot part, extends in described the first slot part around the winding part of the described first toothed region of radially extending the first staor winding around; Winding part around the described second toothed region of radially extending the second staor winding is around extended in described the second slot part; Described the 3rd slot part is between described the first slot part and described the second slot part, and it defines refrigerant flow path.
According to one embodiment of the invention, variable speed scroll compressor further comprises the refrigerant suction port of leading to low pressure volume.
According to one embodiment of the invention, variable speed scroll compressor is configured to force the flow through refrigerant flow path of described groove of at least a portion of the refrigeration agent that enters refrigerant suction port, thus cooling staor winding and permanent magnet.
According to one embodiment of the invention, the ratio of the cross sectional area sum of refrigerant flow path and the cross sectional area of stator, between 3% to 14%, preferably between 5% to 10%, and can be for example between 6% to 8%.This stator cross sectional area does not comprise the central opening for holding rotor.
According to one embodiment of the invention, motor is variable-speed motor.
This variable speed scroll compressor also can further comprise the intermediate jacket around stator.Described intermediate jacket defines at least one inner cavity chamber and defines volume outside annular together with closure, the first winding head that described inner cavity chamber comprises the described stator pointing to towards described high pressure volume.
According to one embodiment of the invention, this variable speed scroll compressor can further comprise the fixed component for stator core body being fixed to closure.Described intermediate jacket is formed by cap, and described cap has covered the end of the sensing high pressure volume of stator core body.
This variable speed scroll compressor can further comprise feedway, and described feedway is for being transported to inner cavity chamber by least a portion of the refrigeration agent that enters refrigerant suction port.According to one embodiment of the invention, feedway comprises that the inlet opening that is arranged in cap and described inlet opening are facing to refrigerant suction port.
According to one embodiment of the invention, motor is arranged in intermediate jacket completely, and intermediate jacket is arranged on low pressure volume and the separated support frame of high pressure volume.
According to one embodiment of the invention, this variable speed scroll compressor also comprises centering member.Described centering member is fixed to closure, and the end back to high pressure volume of intermediate jacket is fixed on described centering member.This centering member and intermediate jacket define the second inner cavity chamber.The second winding head that this second inner cavity chamber comprises the stator being oppositely arranged with the first winding head.This centering member is also provided with at least one refrigeration agent that leads to the second inner cavity chamber and passes through hole.
According to one embodiment of the invention, rotor adopts the mode of slip cooperating relationship to be slidably mounted on live axle, this slip cooperating relationship be arranged to allow occur between rotor and live axle limited relative angle to and/or axial sliding movement.In other words, rotor is to be arranged on live axle with mode axial and/or angle play (or gap).
According to one embodiment of the invention, centering member is provided with guide bearing, and described guide bearing setting is in order to guide the end back to compression unit of live axle.
According to one embodiment of the invention, this variable speed scroll compressor also comprises the locking member that is suitable for live axle to be connected to rotationally described rotor.Described locking member for example can be made up of nonmagnetic substance.
For example, the outer surface of described live axle has the first longitudinal fluting, and the internal surface of described rotor has the second longitudinal fluting, and described the first and second longitudinal flutings circumferentially align, and described locking member extends in described the first and second longitudinal flutings.Described locking member can be suitable for allowing limited relative angle occurring to sliding movement between described rotor and described live axle.
According to an aspect of the present invention, within locking member is slidably mounted at least one of described the first and second longitudinal flutings.
According to an aspect of the present invention, the cross-sectional sizes of the cross-sectional sizes of described locking member and described the first and second longitudinal flutings be suitable for allowing occurring between described rotor and described live axle limited to axial and/or angle sliding movement.
According to one embodiment of the invention, this variable speed scroll compressor also comprises the positioning element being fixed on described live axle.Described positioning element has axial stop surface, and described axial stop surface is arranged to be slidably matched with the end back to described compression unit of described rotor.Described positioning element can be the positioning ring that is fixed to described live axle.
According to one embodiment of the invention, described positioning element thermal shrinkage formula is assembled to live axle.For example, positioning element can be made up of nonmagnetic substance.
According to an aspect of the present invention, in use, basic vertical extension of live axle.
According to one embodiment of the invention, the underpart of rotor is stayed and is leaned against in the axial stop surface of positioning element.
By reading following description and with reference to the accompanying drawing of enclosing, will understand these and other advantage of the present invention.In these accompanying drawings, show according to two of variable speed scroll compressor of the present invention embodiments in the mode of non-limiting example.
Accompanying drawing explanation
Read together by reference to the accompanying drawings and will understand better the following embodiment who describes in detail of the present invention.But, it should be understood that, the present invention is not limited to disclosed specific embodiment.
Fig. 1 is according to the longitudinal sectional drawing of the swirl type cold compressor of first embodiment of the invention.
Fig. 2 is the enlarged view of the detail section of Fig. 1.
Fig. 3 is the enlarged view of the detail section of Fig. 2.
Fig. 4 is the stereogram after the decomposition of detail section of the refrigeration compressor in Fig. 1.
Fig. 5 is the stereogram of the different elements shown in Fig. 4.
Fig. 6 is according to the transverse cross-sectional view of the swirl type cold compressor shown in Fig. 1.
Fig. 7 is according to the plan view of the stator core body of the swirl type cold compressor shown in Fig. 1 and rotor core body.
Fig. 8 is according to the longitudinal sectional drawing of the swirl type cold compressor of second embodiment of the invention.
Embodiment
Fig. 1 shows a kind of swirl type cold compressor 2 of vertical placement.But, without its structure is made to obvious change in the situation that, also can slant setting or horizontal positioned according to refrigeration compressor 2 of the present invention.
Refrigeration compressor 2 shown in Fig. 1 comprises the closure 3 being limited by housing 4.The top of housing 4 and bottom are sealed by top cover 5 and base 6 respectively.
Refrigeration compressor 2 also comprises the support frame 7 being fixed in closure 3, and described closure 3 and support frame 7 have defined low pressure volume.
Refrigeration compressor 2 also comprises the scroll compression unit 8 that is arranged in support frame 7 tops.Described scroll compression unit 8 have cooperatively interact determine scroll element 9 and moving scroll element 11.Especially, moving scroll element 11 by the upper side supporting of support frame 7 and can with the upper side sliding contact of support frame 7, determine scroll element 9 and fix with respect to closure 3.Determine scroll element 9 and can for example be fixed to support frame 7.
Be known that determining scroll element 9 has end plate 12 and scroll 13.Scroll 13 is stretched to moving scroll element 11 from end plate 12; Moving scroll element 11 has end plate 14 and scroll 15.Scroll 15 is stretched to and is determined scroll element 9 from end plate 14.The scroll 15 of moving scroll element 11 and to determine the scroll 13 of scroll element 9 interlaced to form multiple compression chamber 16 between them.Compression chamber 16 has variable volume, wherein, is made track when movable when moving scroll element 11 drives with respect to determining scroll element 9, and the volume of compression chamber 16 reduces toward interior from outer.The end plate 12 of determining scroll element 9 comprises tap hole 17 in heart position therein.This tap hole 17 leads to central compression chamber 16 and leads to high-pressure discharge chamber 18.
Refrigeration compressor 2 also comprises refrigerant suction port 19 and exhaust outlet 20.Suction port 19 leads to low pressure volume compressor is implemented to the supply of refrigeration agent, and 20 of described exhaust outlets lead to discharge chamber 18.
Refrigeration compressor 2 also comprises the variable-speed motor that is arranged in support frame 7 belows (, in low pressure volume).The stator 22 that this motor has rotor 21 and arranges around rotor 21.
As shown in Figure 7, rotor 21 comprises rotor stack or rotor core body 23 and permanent magnet 25.Rotor core body 23 offers axial passage 24.25 of described permanent magnets are inserted in the cannelure being opened in rotor core body 23.Permanent magnet 25 is for example arranged in axial passage 24 around regularly.
As shown in Figures 6 and 7, stator 22 comprises stator stack or stator core body 26 and around the staor winding 27 on stator core body 26.Stator core body 26 therein circumference is provided with the cannelure 29 forming between multiple toothed region 28 of radially extending and multiple toothed region of radially extending at these 28.According to the present invention, each staor winding 27 is by directly around the toothed region 28 of each correspondence, and extends in the cannelure 29 forming in the both sides of corresponding toothed region 28.Each groove 29 comprises the first slot part, the second slot part and the 3rd slot part.Wherein, the winding part of the first adjacent staor winding 27 is extended in the first slot part; The winding part of the second adjacent staor winding 27 is extended in the second slot part; The 3rd slot part is between the first and second slot parts, and it defines refrigerant flow path 30.
In addition, refrigeration compressor 2 comprises live axle 31, and described live axle 31 is suitable for driving and makes scroll element 11 do orbiting.Live axle 31 extends into the axial passage 24 of rotor 21 and is connected to rotationally rotor 21, so that live axle 31 is driven around pivot axis by rotor 21.
The bottom of live axle 31 drives oil pump 34.Oil pump 34 will be supplied to the grease channel 35 in the core that is formed on live axle 31 from the oil of fuel tank (being limited by closure 3).
This refrigeration compressor 2 also comprises the positioning ring 36 that is fixed to live axle 31.Described positioning ring 36 is for example filled to live axle 31 by thermal contraction mode.Positioning ring 36 can be made up of nonmagnetic substance.
Positioning ring 36 has axial stop surface 37, and the underpart of rotor 21 (saying more accurately the radial abutment surface 38 on the underpart of rotor 21) just stayed and leaned against on this stop surface.Therefore, positioning ring 36 is arranged to axially locating rotor 21.
As shown in Figures 2 and 3, refrigeration compressor 2 comprises and is arranged on the first ring shaped axial abutment surface 39 on rotor 21 and is arranged on the second ring shaped axial abutment surface 41 on live axle 31.As Fig. 3 specifically illustrates, between the first and second axial abutment surfaces 39 and 41, can leave predetermined axial clearance, thereby allow, between rotor 21 and live axle 31, limited sliding movement to axial occurs.This predetermined axial clearance can be for example between several microns to 1 millimeter.
Especially, the first ring shaped axial abutment surface 38 is arranged on the upper-end surface of rotor 21, and live axle 31 has the radially end difference that defines the second ring shaped axial abutment surface 39.The first and second ring shaped axial abutment surfaces 38,39 are provided for preventing that rotor 21 from exceeding precalculated position with respect to live axle 31 towards compression unit 8 axial motions.
Refrigeration compressor 2 also comprises stop pin 42.This stop pin 42 is suitable for live axle 31 to be connected to rotationally rotor 21.Stop pin 42 can be for example made up of nonmagnetic substance.
Stop pin 42 extends into respectively the first longitudinal fluting 43 on the outer surface that is opened in live axle 31 and is opened in the second longitudinal fluting 44 on the internal surface of rotor core body 23.This first and second longitudinal fluting 43,44 circumferentially aligns.The cross-sectional sizes of the cross-sectional sizes of stop pin 42 and the first and second longitudinal flutings 43,44 make can allow to occur between rotor 21 and live axle 31 limited to axial with angle sliding movement.Stop pin 42 can be a bit larger tham the first longitudinal fluting 43, and stop pin 42 can be pressed into and be assemblied in the first longitudinal fluting 43 thus, and stop pin 42 is slidably assemblied in the second longitudinal fluting 44.But alternately, stop pin 42 also can be slidedly assemblied in the first and second longitudinal flutings 43,44.
The second longitudinal fluting 44 being arranged on rotor 21 can extend along the whole length of rotor core body 23.Advantageously, the partial-length of the first 43 of longitudinal flutings along live axle 31 extends, and limits axial stop surface 45 for the upper end of stop pin 42.Further, the axial stop surface 37 being arranged on positioning ring 36 has also formed the axial stop for the lower end of stop pin 42.
Refrigeration compressor 2 also can comprise annular fixed component 46 and centering member 47.This annular fixed component 46 is for being fixed to closure by stator 22.This centering member 47 is fixed to closure 3 and is provided with guide bearing 40.Guide bearing 40 is provided for guiding the underpart of live axle 31.
Refrigeration compressor 2 also comprises around stator 22 and has covered the intermediate jacket 48 of the upper end of motor.This intermediate jacket 48 and closure 3 define the outer volume 49 of annular, and refrigerant suction port 19 is just led to the outer volume 49 of this annular.Intermediate jacket 48 defines inner cavity chamber 50 together with motor.The winding head 27a that this inner cavity chamber 50 comprises the stator 22 pointing to towards scroll compression unit 8.The part that the end face 26a towards compression unit 8 from stator core body 26 of staor winding 27 extends has laterally formed described winding head 27a.
In the time of work, the first portion of the refrigeration agent entering by refrigerant suction port 19 flows into the outer volume 49 of annular, and then directly upwards flows to turbine compression unit 8 via refrigeration agent by hole 52.
In addition, the second portion that enters the refrigeration agent of refrigerant suction port 19 flows into inner cavity chamber 50 by the inlet opening 51 of intermediate jacket 48, and then flows through the refrigerant flow path 30(that defined by stator core body 26 and staor winding 27 as shown in Figure 6) flow to centering member 47 downwards.A part that it should be noted in the discussion above that the refrigeration agent that enters into inner cavity chamber 50 also may flow to centering member 47 downwards by the gap 54 of defining between stator core body 26 and rotor core body 23.The refrigerant cools staor winding 27 of the refrigerant flow path of flowing through 30.Meanwhile, flow through refrigerant cools stator core body 26 and the rotor core body 23 in gap 54.So just can protect the permanent magnet of stator core body, rotor core body and rotor core body to make it avoid damaging.
Next, refrigeration agent upwards flows through low pressure volume and enters compression chamber 16 via refrigeration agent by hole 52 towards scroll compression unit 8.
Then, the refrigeration agent that enters scroll compression unit 8 in compression chamber 16 compressed and tap hole 17 by leading to discharge chamber 18 from determine scroll element 9 and moving scroll element 11 in the middle of overflow, the refrigeration agent after the compression in discharge chamber 18 is discharged from by exhaust outlet 20.
Fig. 8 shows the swirl type cold compressor 2 according to second embodiment of the invention.In this swirl type cold compressor 2 and Fig. 1-7, the main difference part of disclosed refrigeration compressor is: its motor is arranged in intermediate jacket 48 completely; Intermediate jacket 48 and motor define near-end chamber 55a and far-end chamber 55b.Wherein, the winding head 27a that near-end chamber 55a comprises the stator 22 pointing to towards scroll compression unit 8, far-end chamber 55b comprises the winding head 27b with the stator 22 of the opposing setting of the first winding head 27a.The part of extending laterally from the opposing end face 26b of stator core body 26 and end face 26a of staor winding 27 has formed described winding head 27b.
According to this second embodiment, the upper end of intermediate jacket 48 is fixed to support frame 7, and the lower end of intermediate jacket 48 is fixed to centering member 47.Like this, intermediate jacket 48 has played the effect of fixed stator core body 26.It should be noted in the discussion above that and also can between intermediate jacket 48 and stator 22, arrange annular connecting element 56.
In addition,, according to the second embodiment, centering member 47 is also provided with towards at least one refrigeration agent of far-end chamber 55b and passes through hole 57.
In the time of work, the refrigeration agent entering by refrigerant suction port 19 flows to centering member 47 downwards outside annular in volume 49.Then, refrigeration agent is flowed through and is arranged on refrigeration agent in centering member 47 by hole 57, and enters distal chamber chamber 55b.Enter into refrigerant flow path 30, the near-end chamber 55a that the refrigeration agent of far-end chamber 55b defines via stator core body 26 and staor winding 27 and the refrigeration agent that is arranged on support frame 7 and upwards flowed to scroll compression unit 8 by hole (Fig. 8 is not shown).It should be noted in the discussion above that the gap (Fig. 8 is not shown) that the part of the refrigeration agent that enters into far-end chamber 55b is likely made by the outer perimeter of intermediate jacket 48 and stator 22 upwards flows to scroll compression unit 8.
Next, the refrigeration agent that enters scroll compression unit 8 in compression chamber 16 compressed and tap hole 17 by leading to discharge chamber 18 from determine scroll element 9 and moving scroll element 11 in the middle of overflow, the refrigeration agent after the compression in discharge chamber 18 is discharged from by exhaust outlet 20.
Certainly, the invention is not restricted to the above embodiment who describes by non-limiting example, but contained on the contrary all possible mode of execution.
Claims (9)
1. a variable speed scroll compressor (2), comprises
-comprise the closure (3) of low pressure volume and high pressure volume;
-be suitable for the compression unit (8) of compressed refrigerant;
-be arranged in described low pressure volume and comprise rotor (21) and the motor of stator (22), described rotor (21) comprises permanent magnet (25), described stator (22) comprises stator core body (26) and staor winding (27), described stator core body (26) be provided with multiple radially extend toothed region (28) and multiple being formed on described in radially extension toothed region (28) between groove (29), described staor winding (27) is upper around described toothed region (28) of radially extending, and each staor winding (27) is in the toothed region (28) of each correspondence;
-being suitable for driving the live axle (31) of described compression unit (8), described live axle (31) is connected to described rotor (21) rotationally, and
-be arranged on the first axial abutment surface (39) on described rotor (21) and be arranged on the second axial abutment surface (41) on described live axle (31), between the described first axial abutment surface (39) and the described second axial abutment surface (41), leave predetermined axial clearance, in order to allow, between described rotor (21) and described live axle (31), limited sliding movement to axial occurs
Wherein, at least one groove (29) forming between the first and second adjacent toothed region (28) of radially extending comprises the first slot part, the second slot part and the 3rd slot part, extends in described the first slot part around the winding part of the first toothed region (28) of radially extending the first staor winding (27) around; Winding part around the second toothed region (28) of radially extending the second staor winding (27) is around extended in described the second slot part; Described the 3rd slot part is between described the first slot part and described the second slot part, and it defines refrigerant flow path (30).
2. variable speed scroll compressor according to claim 1 (2), is characterized in that, the ratio of the cross sectional area sum of described refrigerant flow path and the cross sectional area of stator is between 3% to 14%.
3. variable speed scroll compressor according to claim 1 and 2 (2), it is characterized in that, described variable speed scroll compressor is configured to force the flow through refrigerant flow path (30) of described groove (29) of at least a portion of the refrigeration agent that enters refrigerant suction port.
4. according to the variable speed scroll compressor (2) described in any one in claim 1-3, characterized by further comprising the intermediate jacket (48) around described stator (22), described intermediate jacket (48) defines at least one inner cavity chamber (50,55a) and define the outer volume (49) of annular, the first winding head (27a) that described inner cavity chamber comprises the described stator (22) pointing to towards described high pressure volume together with closure (3).
5. according to the variable speed scroll compressor (2) described in any one in claim 1-4, characterized by further comprising the locking member (42) that is suitable for described live axle (31) to be connected to rotationally described rotor (21).
6. variable speed scroll compressor according to claim 5 (2), it is characterized in that, the outer surface of described live axle (31) has the first longitudinal fluting (43), the internal surface of described rotor (21) has the second longitudinal fluting (44), described the first longitudinal fluting (43) and the second longitudinal fluting (44) circumferentially align, and described locking member (42) extends in described the first longitudinal fluting (43) and the second longitudinal fluting (44).
7. according to the variable speed scroll compressor (2) described in claim 5 or 6, it is characterized in that, described locking member (42) is suitable for allowing limited relative angle occurring to sliding movement between described rotor (21) and described live axle (31).
8. according to the variable speed scroll compressor (2) described in any one in claim 1-7, characterized by further comprising the positioning element (36) being fixed on described live axle (31), described positioning element (36) has axial stop surface (37), and described axial stop surface (37) is arranged to be slidably matched with the end back to described compression unit (8) of described rotor (21).
9. variable speed scroll compressor according to claim 8 (2), is characterized in that, described positioning element (36) is for being fixed to the positioning ring of described live axle.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FR12/60989 | 2012-11-19 | ||
| FR1260989A FR2998340A1 (en) | 2012-11-19 | 2012-11-19 | SPIRAL COMPRESSOR WITH VARIABLE SPEED. |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103821718A true CN103821718A (en) | 2014-05-28 |
Family
ID=47628200
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310581293.2A Pending CN103821718A (en) | 2012-11-19 | 2013-11-18 | Variable speed scroll compressor |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20140140867A1 (en) |
| CN (1) | CN103821718A (en) |
| DE (1) | DE102013019110A1 (en) |
| FR (1) | FR2998340A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105927524A (en) * | 2016-04-19 | 2016-09-07 | 广东美的制冷设备有限公司 | Control method and device for compressor and air conditioner |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1174594A (en) * | 1995-10-17 | 1998-02-25 | 大金工业株式会社 | Refrigerant compressor |
| US20010012489A1 (en) * | 1999-12-21 | 2001-08-09 | Yoshiaki Harakawa | Sealed-type electric compressor having refrigerant passage |
| CN1802506A (en) * | 2003-06-09 | 2006-07-12 | 大金工业株式会社 | Compressor |
| CN101004174A (en) * | 2006-01-20 | 2007-07-25 | 株式会社丰田自动织机 | Electric pump for hydrogen circulation |
| CN101223364A (en) * | 2005-05-23 | 2008-07-16 | 丹佛斯商业压缩机公司 | Compresseur frigorifique a spirales |
| US7737592B2 (en) * | 2007-01-19 | 2010-06-15 | Nidec Corporation | Motor |
| JP4841536B2 (en) * | 2007-11-30 | 2011-12-21 | 三菱電機株式会社 | Motor and refrigerant compressor provided with the same |
| CN102444580A (en) * | 2010-09-30 | 2012-05-09 | 艾默生电气公司 | Digital compressor with directly started brushless permanent magnet motor |
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| JPS5832990A (en) * | 1981-08-24 | 1983-02-26 | Hitachi Ltd | Screw compressor |
| US4792713A (en) * | 1987-10-16 | 1988-12-20 | Onan Corporation | Lamination to rotor shaft retention method utilizing spring pins |
| JPH0765578B2 (en) * | 1988-12-07 | 1995-07-19 | 三菱電機株式会社 | Scroll compressor |
| JP3936105B2 (en) * | 1999-08-11 | 2007-06-27 | 東芝キヤリア株式会社 | Compressor |
| JP4036148B2 (en) * | 2002-07-23 | 2008-01-23 | 株式会社豊田自動織機 | Electric motor and electric compressor |
| JP4175148B2 (en) * | 2003-03-12 | 2008-11-05 | 松下電器産業株式会社 | Hermetic compressor |
| JP5050393B2 (en) * | 2006-04-19 | 2012-10-17 | ダイキン工業株式会社 | Compressor |
| GB0702997D0 (en) * | 2007-02-16 | 2007-03-28 | Rolls Royce Plc | A cooling arrangement of an electrical machine |
| JP5612411B2 (en) * | 2010-09-21 | 2014-10-22 | 株式会社ヴァレオジャパン | Scroll compressor |
-
2012
- 2012-11-19 FR FR1260989A patent/FR2998340A1/en not_active Withdrawn
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2013
- 2013-11-14 DE DE102013019110.6A patent/DE102013019110A1/en not_active Withdrawn
- 2013-11-18 CN CN201310581293.2A patent/CN103821718A/en active Pending
- 2013-11-19 US US14/084,152 patent/US20140140867A1/en not_active Abandoned
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1174594A (en) * | 1995-10-17 | 1998-02-25 | 大金工业株式会社 | Refrigerant compressor |
| US20010012489A1 (en) * | 1999-12-21 | 2001-08-09 | Yoshiaki Harakawa | Sealed-type electric compressor having refrigerant passage |
| CN1802506A (en) * | 2003-06-09 | 2006-07-12 | 大金工业株式会社 | Compressor |
| CN101223364A (en) * | 2005-05-23 | 2008-07-16 | 丹佛斯商业压缩机公司 | Compresseur frigorifique a spirales |
| CN101004174A (en) * | 2006-01-20 | 2007-07-25 | 株式会社丰田自动织机 | Electric pump for hydrogen circulation |
| US7737592B2 (en) * | 2007-01-19 | 2010-06-15 | Nidec Corporation | Motor |
| JP4841536B2 (en) * | 2007-11-30 | 2011-12-21 | 三菱電機株式会社 | Motor and refrigerant compressor provided with the same |
| CN102444580A (en) * | 2010-09-30 | 2012-05-09 | 艾默生电气公司 | Digital compressor with directly started brushless permanent magnet motor |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105927524A (en) * | 2016-04-19 | 2016-09-07 | 广东美的制冷设备有限公司 | Control method and device for compressor and air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| US20140140867A1 (en) | 2014-05-22 |
| DE102013019110A1 (en) | 2014-05-22 |
| FR2998340A1 (en) | 2014-05-23 |
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Application publication date: 20140528 |