CN207195176U - Back pressure cavity configuration and there is its scroll compressor - Google Patents

Abstract

The utility model provides a kind of back pressure cavity configuration and has its scroll compressor.The back pressure cavity configuration includes：First back pressure chamber, the first drainage channel, the second back pressure chamber and the second drainage channel, the first back pressure chamber are arranged on the first area between the orbiter of screw compressor and support；First drainage channel connects the compression chamber of screw compressor with the first back pressure chamber so that the fluid from compression chamber applies the first back pressure to orbiter；Second back pressure chamber is arranged on the second area between orbiter and support；Second drainage channel connects discharge chamber with the second back pressure chamber so that the fluid from discharge chamber applies the second back pressure to orbiter；Wherein, first area and second area are spaced different zones, and along the radial direction of orbiter, first area is located at the inner side of second area.Solve the problems, such as the orbiter back pressure surplus of scroll compressor of the prior art or back pressure deficiency.

Description

Back pressure cavity configuration and there is its scroll compressor

Technical field

Compressor field is the utility model is related to, in particular to a kind of back pressure cavity configuration and there is its vortex Compressor.

Background technology

Screw compressor is that a kind of efficiency high, noise be low and the positive displacement compressor of smooth running, extensively should in recent years For in air-conditioning and refrigeration unit.In general, screw compressor is by sealing shell, orbiter, fixed scroll, bent axle, anti- The parts such as free-wheeling system and motor form.It forms several to crescent moon Shape closed by a pair of intermeshing dynamic and static scroll wraps Working chamber.Under bent axle driving, orbiter makees the translation without rotation, the moon around fixed scroll center to fix the radius of gyration Tooth working chamber constantly moves to center, and its volume constantly reduces and pressure constantly raises, until being communicated with central exhaust port, high pressure Refrigerant is discharged the pump housing.

In the screw compressor course of work, because gas force, centrifugal action are on orbiter, it is set to topple or depart from Fixed scroll causes gas leakage or friction aggravation.Therefore, the balance of orbiter axial gas power is screw compressor reality The key technology of existing high efficiency and high reliability.

Scroll compressor of the prior art is by the way that discharge chamber or compression chamber air-flow are guided to the back of the body of orbiter The axial gas dynamic balance of orbiter is realized in pressure side, to reach the purpose of axial seal.

Certain technological deficiency be present in above-mentioned technical proposal.Specifically, only the high pressure draught of discharge chamber is guided to dynamic whirlpool The back pressure side of capstan, when pressure at expulsion is too high, the back pressure of orbiter is superfluous, and orbiter connects with fixed scroll end Touch pressure is excessive, causes orbiter and the increase of fixed scroll friction power loss even inordinate wear occurs, surface-treated layer comes off The problems such as, directly affect compressor performance and reliability；And only the middle pressure gas stream of compression chamber is guided to the back pressure of orbiter Side, it may appear that the hypodynamic situation of back pressure, cause compression chamber gas to leak.

Utility model content

Main purpose of the present utility model is to provide a kind of back pressure cavity configuration and has its scroll compressor, so that Solve the problems, such as scroll compressor back pressure surplus or back pressure deficiency of the prior art less.

To achieve these goals, according to one side of the present utility model, there is provided a kind of back pressure cavity configuration, back pressure Cavity configuration includes：First back pressure chamber, the first area being arranged between the orbiter of screw compressor and support；First drainage Passage, the first end of the first drainage channel connect with the compression chamber of screw compressor, and the second end of the first drainage channel extends to First back pressure chamber is so that the fluid from compression chamber applies the first back pressure by the first back pressure chamber to orbiter；Second back pressure Room, the second area being arranged between orbiter and support；Second drainage channel, the first end and vortex of the second drainage channel The discharge chamber connection of compressor, the second end of the second drainage channel extends to the second back pressure chamber so that the fluid from discharge chamber leads to Cross the second back pressure chamber and apply the second back pressure to orbiter；Wherein, first area and second area are spaced difference Region, along the radial direction of orbiter, first area is located at the inner side of second area.

Further, support includes：Master body；First annular flange, master body is arranged on along the circumferentially extending of master body End face on, and towards orbiter protrude set；Wherein, first area is main disk body, first annular flange and dynamic vortex The annular compartment of armor synthesis.

Further, support also includes：Second annular flange, master body is extended on around the periphery of first annular flange End face on, and towards orbiter protrude set；Wherein, second area is main disk body, first annular flange, the second convex annular The annular compartment that edge and orbiter enclose.

Further, back pressure cavity configuration also includes：Floating seal assembly, along being arranged on being axially moveable work for orbiter In second back pressure chamber, the second back pressure chamber is sealed；Floating seal assembly the fluid from discharge chamber pressure effect under with At least part aft bulkhead of orbiter is abutted to apply the second back pressure and by the first back pressure chamber and scroll compression to orbiter The suction muffler isolating seal of contracting machine.

Further, floating seal assembly includes：Floating seal ring, the is arranged on being axially moveable work along orbiter To apply the second back pressure, the first end face of floating seal ring and at least part of orbiter to orbiter in two back pressure chambers Aft bulkhead abuts, and the second end face of floating seal ring is relative with support；Wherein, first end face and second end face are floating seal ring Two relative end faces.

Further, floating seal assembly also includes：Wear plate, it is folded in the first end face and dynamic vortex of floating seal ring With by the suction muffler isolating seal of the first back pressure chamber and screw compressor between at least part aft bulkhead of disk.

Further, the first seal groove is offered along the circumference of the inner ring of floating seal ring, is arranged with the first seal groove First sealing ring with by the second back pressure chamber seal.

Further, the second seal groove is offered along the circumference of the outer ring of floating seal ring, is arranged with the second seal groove Second sealing ring with by the second back pressure chamber seal.

Further, the first seal groove and the second seal groove are to be opened in floating seal ring along the recessed of its axial middle part Fall into groove or be opened in the step groove of the second end face of floating seal ring.

Further, flow-guiding channel is offered on floating seal ring and orbiter, the fluid in the second back pressure chamber is through leading Circulation road is flowed into the first back pressure chamber, or is flowed into through flow-guiding channel in compression chamber or in suction muffler.

Further, flow-guiding channel includes the throttling oil supplying hole being opened on floating seal ring, and throttling oil supplying hole edge is floated Sealing ring it is axially extending, to connect the first end face of floating seal ring and second end face.

Further, flow-guiding channel also includes the guiding gutter being opened on orbiter, and guiding gutter is arranged on orbiter Aft bulkhead on and for throttling oil supplying hole connect.

Further, orbiter has first position and the second of the fixed scroll movement relative to screw compressor Put；When orbiter is moved to first position, throttling oil supplying hole is connected by guiding gutter with the first back pressure chamber；Orbiter moves During to the second place, throttling oil supplying hole connects with compression chamber or suction muffler；Wherein, when orbiter is moved to first position, pressure Contracting chamber separates so that compression chamber is in compressive state with suction muffler；When orbiter is moved to the second place, compression chamber and air-breathing Chamber is connected so that compression chamber is in suction condition.

Further, the compression chamber oil supply gallery connected with compression chamber is offered on orbiter；Orbiter is moved to During first position, compression chamber oil supply gallery is connected so that the fluid in the second back pressure chamber passes through the oil supplying hole that throttles with throttling oil supplying hole Compression chamber is flowed into compression chamber oil supply gallery.

Further, floating seal assembly also includes：Throttle pressure limiting valve, is arranged in throttling oil supplying hole, for flowing through The fluid of throttling oil supplying hole is throttled and is depressured；Wherein, throttle pressure limiting valve entrance point towards the second back pressure chamber set, with resistance The reverse flow of fluids only to throttle in oil supplying hole is returned in the second back pressure chamber.

Further, floating seal ring includes：First ring body and the second ring body, the first ring body and the second ring body are removably Connection；Wherein, offer on the end face that the second ring body is used to be connected with the first ring body and determine along the axis extension of throttling oil supplying hole Position hole, throttling pressure limiting valve are arranged in positioning hole.

Further, back pressure cavity configuration also includes：3rd drainage channel, one end and the first back pressure chamber of the 3rd drainage channel Connection, the other end of the 3rd drainage channel connect with the second back pressure chamber, by the fluid conduction in the first back pressure chamber to second back of the body In pressure chamber.

Further, back pressure cavity configuration also includes：First unidirectional stop valve, the first unidirectional stop valve are arranged on the 3rd drainage In passage, the entrance point of the first unidirectional stop valve is set towards the first back pressure chamber, so that the 3rd drainage channel is by the first back pressure chamber To the second back pressure chamber one-way conduction.

Further, back pressure cavity configuration also includes：Second unidirectional stop valve, the second unidirectional stop valve are arranged on the second drainage In passage, the entrance point of the second unidirectional stop valve is set towards discharge chamber, so that the second drainage channel is carried on the back from discharge chamber to second Pressure chamber one-way conduction.

Further, the bottom of discharge chamber has reserve, and the first end of the second drainage channel connects with reserve.

Further, the first drainage channel is opened on orbiter along the axial direction of orbiter.

According to second of the present utility model aspect, there is provided a kind of scroll compressor, including back pressure cavity configuration, back pressure Cavity configuration is the back pressure cavity configuration of the above.

Using the back pressure cavity configuration of technical solutions of the utility model, including：First back pressure chamber, the first drainage channel, second Back pressure chamber and the second drainage channel, the first back pressure chamber are arranged on the firstth area between the orbiter of screw compressor and support Domain；The first end of first drainage channel connects with the compression chamber of screw compressor, and the second end of the first drainage channel extends to One back pressure chamber is so that the fluid from compression chamber applies the first back pressure by the first back pressure chamber to orbiter；Second back pressure chamber The second area being arranged between orbiter and support；The first end of second drainage channel and the discharge chamber of screw compressor connect It is logical, the second end of the second drainage channel extend to the second back pressure chamber so that the fluid from discharge chamber by the second back pressure chamber to dynamic Scroll plate applies the second back pressure；Wherein, first area and second area are spaced different zones, along orbiter Radially, first area is located at the inner side of second area.So as to use binary channels respectively by the compression chamber and high pressure of intermediate pressure The high-pressure fluid of discharge chamber guide to the back pressure side of orbiter, back pressure caused by the high pressure fluid from discharge chamber It can always be cancelled out each other with the active force of discharge chamber, back pressure caused by the intermediate pressure fluid from compression chamber always can be with Suction muffler, the active force of compression chamber are cancelled out each other, and so as to realize under different pressure ratio working conditions, both may insure each operating mode Pump housing axial seal, while the problem of avoid the occurrence of back pressure surplus.So make it that the first back pressure and the second back pressure are produced Fluctuation is smaller with joint efforts for raw back pressure, makes orbiter operation more stable, can reduce the vibration and noise of screw compressor.Solve Scroll compressor back pressure of the prior art is superfluous or the problem of back pressure deficiency.

In addition to objects, features and advantages described above, the utility model also has other purposes, feature and excellent Point.Below with reference to figure, the utility model is described in further detail.

Brief description of the drawings

A part of Figure of description of the present utility model is formed to be used for providing further understanding to of the present utility model, this The schematic description and description of utility model is used to explain the utility model, does not form to improper limit of the present utility model It is fixed.In the accompanying drawings：

Fig. 1 is the structural representation according to the optional scroll compressor of the utility model embodiment；

Fig. 2 is according to optionally a kind of first drainage channel of back pressure cavity configuration of the utility model embodiment and throttling fuel feeding A kind of working state schematic representation in hole；

Fig. 3 is according to optionally a kind of first drainage channel of back pressure cavity configuration of the utility model embodiment and throttling fuel feeding Another working state schematic representation in hole；

Fig. 4 is according to the optionally a kind of structural representation of back pressure cavity configuration of the utility model embodiment 1；

Fig. 5 is according to the optionally a kind of amplification knot of the floating seal assembly of back pressure cavity configuration of the utility model embodiment 1 Structure schematic diagram；

Fig. 6 is according to the optionally a kind of structural representation of back pressure cavity configuration of the utility model embodiment 2；

Fig. 7 is according to the optionally a kind of amplification knot of the floating seal assembly of back pressure cavity configuration of the utility model embodiment 2 Structure schematic diagram；

Fig. 8 is according to the optionally a kind of structural representation of back pressure cavity configuration of the utility model embodiment 3；

Fig. 9 is according to the optionally a kind of structural representation of back pressure cavity configuration of the utility model embodiment 4；

Figure 10 is according to the optionally a kind of amplification knot of the floating seal assembly of back pressure cavity configuration of the utility model embodiment 4 Structure schematic diagram；

Figure 11 is according to the optionally a kind of structural representation of back pressure cavity configuration of the utility model embodiment 5；And

Figure 12 is the back pressure surplus and operating mode pressure ratio relation according to the optional scroll compressor of the utility model embodiment Curve synoptic diagram.

Wherein, above-mentioned accompanying drawing marks including the following drawings：

1st, screw compressor；2nd, compression mechanism；3rd, electric machine assembly；4th, it is driven drive mechanism；5th, case component；6th, float close Sealing assembly；10th, suction muffler；11st, compression chamber；12nd, discharge chamber；13rd, the first back pressure chamber；14th, the second back pressure chamber；15th, reserve； 16th, the first drainage channel；17th, the second drainage channel；18th, the 3rd drainage channel；19th, compression chamber oil supply gallery；201st, quiet vortex Disk；202nd, orbiter；203rd, driving bearing；204th, anti-rotation steel ring；205th, exhaust valve component；206th, high-low pressure parting seal Circle；207th, high-pressure channel sealing ring is drawn；208th, fixed scroll draws high-pressure oil gas passage；301st, motor stator；302nd, rotor； 303rd, main balance weight；304th, secondary balance weight；305th, rotor cover plate；306th, rotor cover plate；401st, support；402nd, bent axle；403rd, it is bent Handle pin；404th, eccentric bushing；405th, base bearing；406th, supplementary bearing；407th, anti-rotation straight pin；409th, alignment pin；410th, support draws High-pressure oil gas passage；411st, first annular flange；412nd, the second annular flange；413rd, master body；501st, housing；502nd, end cap； 503rd, oil centrifugal mechanism；504th, filter screen；505th, fastening bolt；506th, air entry；507th, exhaust outlet；508th, oil ease-hole； 509th, end cap draws high-pressure oil gas passage；510th, oily rib is kept off；601st, floating seal ring；602nd, the first sealing ring；603rd, the second sealing Circle；604th, wear plate；605th, the second unidirectional stop valve；606th, the first unidirectional stop valve；607th, throttle pressure limiting valve；608th, first is close Sealing groove；609th, the second seal groove；610th, throttle oil supplying hole；611st, the first ring body；612nd, the second ring body；613rd, positioning hole；701、 Jump ring；702nd, axle envelope.

Embodiment

It should be noted that in the case where not conflicting, the feature in embodiment and embodiment in the utility model can To be mutually combined.Describe the utility model in detail below with reference to the accompanying drawings and in conjunction with the embodiments.

In order that those skilled in the art more fully understand the utility model, it is real below in conjunction with the utility model The accompanying drawing in example is applied, the technical scheme in the embodiment of the utility model is clearly and completely described, it is clear that be described Embodiment is only the embodiment of the utility model part, rather than whole embodiments.Based on the reality in the utility model Example is applied, the every other embodiment that those of ordinary skill in the art are obtained under the premise of creative work is not made, all should When the scope for belonging to the utility model protection.

According to the back pressure cavity configuration of the utility model embodiment, as shown in figure 1, including：First back pressure chamber 13, first drains Passage 16, the second back pressure chamber 14 and the second drainage channel 17, the first back pressure chamber 13 are arranged on the orbiter of screw compressor 1 First area between 202 and support 401；The first end of first drainage channel 16 connects with the compression chamber 11 of screw compressor 1, Second end of the first drainage channel 16 extends to the first back pressure chamber 13 so that the fluid from compression chamber 11 passes through the first back pressure chamber 13 apply the first back pressure to orbiter 202；Second back pressure chamber 14 is arranged between orbiter 202 and support 401 Two regions；The first end of second drainage channel 17 connects with the discharge chamber 12 of screw compressor 1, and the second of the second drainage channel 17 End extends to the second back pressure chamber 14 so that the fluid from discharge chamber 12 applies the by the second back pressure chamber 14 to orbiter 202 Two back pressures；Wherein, first area and second area are spaced different zones, along the radial direction of orbiter 202, first Region is located at the inner side of second area.

Using the back pressure cavity configuration of technical solutions of the utility model, including：First back pressure chamber 13, the first drainage channel 16, Second back pressure chamber 14 and the second drainage channel 17, the first back pressure chamber 13 be arranged on the orbiter of screw compressor 1 and support it Between first area；The first end of first drainage channel 16 connects with the compression chamber 11 of screw compressor 1, the first drainage channel 16 The second end extend to the first back pressure chamber 13 so that the fluid from compression chamber 11 is applied by the first back pressure chamber 13 to orbiter Add the first back pressure；Second back pressure chamber 14 is arranged on the second area between orbiter and support；Second drainage channel 17 First end connects with the discharge chamber 12 of screw compressor 1, the second end of the second drainage channel 17 extend to the second back pressure chamber 14 with The fluid from discharge chamber 12 is set to apply the second back pressure to orbiter by the second back pressure chamber 14；Wherein, first area with Second area is spaced different zones, and along the radial direction of orbiter, first area is located at the inner side of second area.So as to The high-pressure fluid of the compression chamber 11 of intermediate pressure and the discharge chamber 12 of high pressure is guided to orbiter respectively using binary channels Back pressure side, back pressure caused by the high pressure fluid from discharge chamber 12 always can mutually support with the active force of discharge chamber 12 Disappear, back pressure caused by the intermediate pressure fluid from compression chamber 11 always can be with the active force phase of suction muffler, compression chamber 11 Mutually offset, so as to realize under different pressure ratio working conditions, both may insure each operating mode pump housing axial seal, while avoid out The problem of existing back pressure surplus.It is smaller so make it that back pressure caused by the first back pressure and the second back pressure fluctuates with joint efforts, Make orbiter operation more stable, the vibration and noise of screw compressor 1 can be reduced.Solves vortex pressure of the prior art The problem of contracting machine back pressure surplus or back pressure deficiency.

When it is implemented, as shown in Figure 1 to Figure 3, axial direction of first drainage channel 16 along orbiter 202 is opened in dynamic whirlpool On capstan 202, the first end of the first drainage channel 16 connects with compression chamber 11, the second end of the first drainage channel 16 and first back of the body Pressure chamber 13 connects, so that the middle pressure gas stream after overcompression in compression chamber 11 flows to the first back pressure chamber 13, with to dynamic vortex Disk 202 forms the first back pressure.

First back pressure chamber 13 and/or the second back pressure chamber 14 are the circumferential annular chamber of orbitting scroll 202, the first back pressure chamber 13 are arranged at intervals with the second back pressure chamber 14.First back pressure chamber 13 is set close to the axis of orbiter 202, the edge of the second back pressure chamber 14 Set at the circumferential edge of orbiter 202.

Specifically, as shown in figure 4, support 401 includes：Master body 413, the annular flange of first annular flange 411 and second 412, first annular flange 411 is arranged on master body 413 towards the end face of orbiter 202 along the circumferentially extending of master body 413 On, first annular flange 411 protrudes towards orbiter 202 to be set and leaves certain interval between orbiter 202；Second Annular flange 412 is extended on the end face of master body 413 around the periphery of first annular flange 411, the second annular flange 412 Protrude and set towards orbiter 202, the end face of the second annular flange 412 is adjacent to the end face of fixed scroll 201 and by fixed Position pin 409 is fixed together；Wherein, first area is main disk body 413, first annular flange 411 and orbiter 202 The annular compartment that encloses of aft bulkhead, the first back pressure chamber 13 is in the centre of orbiter 202；Based on second area The annular compartment that disk body 413, first annular flange 411, the second annular flange 412 and orbiter 202 enclose, makes second Back pressure chamber 14 is in the circumferential edge position of orbiter 202.By by the compression chamber 11 of intermediate pressure and the exhaust of high pressure The different zones that the high-pressure fluid of chamber 12 is guided to the back pressure side of orbiter 202, which are formed, makes a concerted effort, it is possible to achieve different pressure ratio works Under the conditions of condition, the problem of both having may insure each operating mode pump housing axial seal, while avoided the occurrence of back pressure surplus.So that first back of the body Fluctuation is smaller with joint efforts for back pressure caused by pressure and the second back pressure, makes orbiter operation more stable, can reduce scroll compression The vibration and noise of contracting machine 1.Solve the problems, such as scroll compressor back pressure surplus or back pressure deficiency of the prior art.

As shown in figure 4, the bottom of discharge chamber 12 has reserve 15, filter screen 504 is provided with the second drainage channel 17, the The first end of two drainage channels 17 connects with reserve 15 guides the high pressure refrigeration oil of reserve 15 to back pressure side.

In order to ensure between the sealing of the second back pressure chamber 14 and the first back pressure chamber 13 and the suction muffler 10 of screw compressor 1 Good seal isolation, is provided with floating seal assembly 6 in the second back pressure chamber 14, and floating seal assembly 6 is along orbiter 202 Be arranged in the second back pressure chamber 14 so that the second back pressure chamber 14 to be sealed with being axially moveable work, floating seal assembly 6 is from row The pressure effect of the high-pressure fluid of air cavity 12 is lower to abut with least part aft bulkhead of orbiter 202 and is applied to orbiter 202 Add the second back pressure, ensure the sealing between orbiter 202 and fixed scroll 201 and the stable operation of orbiter 202. The first back pressure chamber 13 is sealed off with suction muffler 10 simultaneously.

As shown in Figures 4 to 7, specifically, floating seal assembly 6 includes：Floating seal ring 601 and wear plate 604, float Sealing ring 601 is arranged in the second back pressure chamber 14 with being axially moveable work along orbiter 202, and the first of floating seal ring 601 End face abuts with least part annular region of the aft bulkhead of orbiter 202, the second end face and support of floating seal ring 601 401 is relative；Wherein, first end face and second end face are two relative end faces of floating seal ring, the aft bulkhead of orbiter 202 End wall for orbiter 202 towards support 401；The second of floating seal ring 601 is acted on from the high-pressure fluid of discharge chamber 12 On end face and floating seal ring 601 is promoted to apply the second back pressure to orbiter 202.

Wear plate 604 is folded between floating seal ring 601 and at least part aft bulkhead of orbiter 202, is played and is subtracted The effect for the frictional force that small orbiter 202 operates, while play a part of the first back pressure chamber 13 and the dynamic sealing of suction muffler 10. The generally use steel band of wear plate 604, usual punch forming, processing technology is simple, and manufacturing cost is low, and flatness and surface are thick Rugosity can obtain preferable precision, so as to reduce the friction power loss between orbiter 202 and wear plate 604.In addition, Advantageously reduce the requirement of the end face machining accuracy of floating seal ring 601.

In order to realize the excellent sealing between the second back pressure chamber 14 and the first back pressure chamber 13, specifically, along floating seal ring The circumference of 601 inner ring offers the first seal groove 608, and the second sealing is offered along the circumference of the outer ring of floating seal ring 601 Groove 609, the first sealing ring 602 is arranged with the first seal groove 608, the second sealing ring 603 is arranged with the second seal groove 609. As shown in Figure 3 and Figure 5, the first seal groove 608 and the second seal groove 609 are to be opened in floating seal ring 601 along its axial direction The recessed groove at middle part or be opened in floating seal ring 601 second end face step groove.Pass through the first sealing ring 602 and second Sealing ring 603 can be effectively by the isolating seal of the second back pressure chamber 14.Alternatively, the first sealing ring 602 and the second sealing ring 603 Can be the type seal elements such as O-ring seals, energy-stored spring sealing ring.

In addition, the first seal groove 608 and the second seal groove 609 can also be opened except that can be opened on floating seal ring 601 It is located on support 401.

As shown in Figure 4 and Figure 5, the first seal groove 608 and the second seal groove 609 are opened in floating seal ring 601 along its The middle part of axial direction.It is as shown in Figure 6 and Figure 7, close floating for the ease of the processing of the first seal groove 608 and the second seal groove 609 Ring-shaped step structure is opened up along its circumference in the second end face of seal ring 601, the ring-shaped step structure and support 401 cooperatively form the One seal groove 608 and the second seal groove 609, that is, it is easy to the first seal groove 608 and the second seal groove 609 to process, also allows for simultaneously The assembling of first sealing ring 602 and the second sealing ring 603.

In order to avoid screw compressor in the course of the work brings a large amount of refrigeration oils in discharge chamber 12 into the condensation of air-conditioning In device or evaporator, the heat exchange of two devices is influenceed, while avoids all parts in the first back pressure chamber 13 and suction muffler 10 from lacking freezing Oil and influence lubrication, further, flow-guiding channel, the second back pressure chamber 14 are offered on floating seal ring 601 and orbiter 202 Interior fluid is flowed into the first back pressure chamber 13 through flow-guiding channel, or flows into screw compressor after flow-guiding channel and compression chamber 11 Compression chamber 11 or suction muffler 10 in.By controlling the position of orbiter 202 and flow-guiding channel, compression is in compression chamber 11 During state, flow-guiding channel is connected with the first back pressure chamber 13, refrigeration oil is back in the first back pressure chamber 13 to lubricate first back of the body Corresponding component in pressure chamber 13；When screw compressor is in suction condition, flow-guiding channel is connected with compression chamber 11, and compress Chamber 11 connects under suction condition with suction muffler 10, so as to make refrigeration oil be back in suction muffler 10 to lubricate by compression chamber 11 Corresponding component in suction muffler 10.

As shown in Figures 2 to 7, flow-guiding channel includes the throttling oil supplying hole 610 being opened on floating seal ring 601 and opened The guiding gutter being located on orbiter 202, throttling oil supplying hole 610 are floated close along the axially extending of floating seal ring 601 with connection The first end face and second end face of seal ring 601, guiding gutter are arranged on the aft bulkhead of orbiter 202, and one end of guiding gutter is prolonged Extend in the first back pressure chamber 13, the other end of guiding gutter extends at the oil supplying hole 610 that throttles and relative with throttling oil supplying hole 610.

Orbiter 202 has the first position and the second place moved relative to fixed scroll 201 in action process； When orbiter 202 is moved to first position, throttling oil supplying hole 610 is connected by guiding gutter with the first back pressure chamber 13；Dynamic vortex When disk 202 is moved to the second place, throttling oil supplying hole 610 connects with compression chamber 11 or suction muffler 10；Wherein, orbiter 202 When being moved to first position, the scrollwork tooth of orbiter 202 is mutually closed so that compression chamber 11 with the scrollwork tooth of fixed scroll 201 Separate with suction muffler 10 so as to be in compressive state；When orbiter 202 is moved to the second place, the scrollwork of orbiter 202 Tooth is mutually opened with the scrollwork tooth of fixed scroll 201 so that compression chamber 11 is connected with suction muffler 10 so as to be in suction condition.

Under being in compressive state in compression chamber 11, the refrigeration oil of high pressure can be introduced in compression chamber 11 to ensure pressure Sufficient lubrication and sealing in contracting chamber 11.Further, connect as shown in figure 8, being offered on orbiter 202 with compression chamber 11 Logical compression chamber oil supply gallery 19；When orbiter 202 is moved to first position, i.e., compression chamber 11 is in the position of compressive state Put, compression chamber oil supply gallery 19 is connected with throttling oil supplying hole 610, and the high pressure refrigeration oil from discharge chamber 12 is passed through into the fuel feeding that throttles Hole 610 and compression chamber oil supply gallery 19 are drained to lubrication and the sealing realized in compression chamber 11 to compression chamber 11.In compression chamber 11 High-pressure fluid is introduced to its inside when under compressive state, the gettering efficiency of screw compressor 1 can be ensured.

In order to carry out current limliting to the high pressure refrigeration oil for flowing into compression chamber 11 by compression chamber oil supply gallery 19, while avoid pressing High-pressure fluid in contracting chamber 11 is to the adverse current of the second back pressure chamber 14, as shown in figure 9, being provided with throttling limit in throttling oil supplying hole 610 Pressure valve 607, throttling pressure limiting valve 607 are used for the high-pressure fluid that convection current is crossed in throttling oil supplying hole 610 and are throttled and be depressured；Wherein, The entrance point of pressure limiting valve 607 of throttling is set towards the second back pressure chamber 14, to prevent the reverse flow of fluids in throttling oil supplying hole 610 from returning the In two back pressure chambers 14.

Throttling pressure limiting valve 607 is assembled in throttling oil supplying hole 610 for convenience, further, as shown in Figure 10, floated Sealing ring 601 includes：First ring body 611 and the second ring body 612, the first ring body 611 and the second ring body 612 can by connecting bolt Releasably link together；Wherein, offer on the end face that the second ring body 612 is used to be connected with the first ring body 611 and supplied along throttling The positioning hole 613 of the axis extension of oilhole 610, throttling pressure limiting valve 607 are arranged in positioning hole 613, and the first ring body 611 is pressed in section Throttling pressure limiting valve 607 is fixed by the spring terminal of ductility limit pressure valve 607.Pressure limiting valve 607 throttle from compression chamber 11 to the second back pressure Room 14 is cut-off direction.

For not setting relief valve in compression chamber 11 or having set relief valve but fail timely and effective pressure release, screw compressor Easily there is overcompression, so as to cause the pressure of the first back pressure chamber 13 to be higher than the pressure of the second back pressure chamber 14, in order to ensure second back of the body Pressure chamber 14 is in highest pressure all the time, so as to maintain the back pressure to the circumferential edge of orbiter 202, to ensure to compress The sealing of chamber 11, further, as shown in figure 11, back pressure cavity configuration also includes：3rd drainage channel 18, the 3rd drainage channel 18 one end connects with the first back pressure chamber 13, and the other end of the 3rd drainage channel 18 connects with the second back pressure chamber 14, by first In fluid conduction to the second back pressure chamber 14 in back pressure chamber 13；The first unidirectional stop valve is provided with the 3rd drainage channel 18 606, the oil inlet end of the first unidirectional stop valve 606 is set towards the first back pressure chamber 13, to prevent the fluid in the second back pressure chamber 14 Flow into the first back pressure chamber 13.That is the second back pressure chamber 14 is cut-off direction to the first back pressure chamber 13, overcompression occurs in compressor In the case of, the fluid of elevated pressures enters the second back pressure chamber 14 by the 3rd drainage channel 18 in the first back pressure chamber 13, makes the Two back pressure chambers 14 are in maximum pressure all the time, ensure effective sealing of the pump housing axial direction in the case of overcompression.

In the case where overcompression occurs in compressor, in order to prevent the high-pressure fluid in the second back pressure chamber 14 to be back to exhaust In chamber 12, further, as shown in figure 11, the second unidirectional stop valve 605 is provided with the second drainage channel 17, second is unidirectional The entrance point of stop valve 605 is set towards discharge chamber 12, i.e., is cut-off direction from the second back pressure chamber 14 to discharge chamber 12, so as to hinder Only the fluid of the second back pressure chamber 14 is flowed back in discharge chamber 12.

According to second embodiment of the present utility model, there is provided a kind of scroll compressor, including back pressure cavity configuration, should Back pressure cavity configuration is the back pressure cavity configuration of above-described embodiment.Adopted using the scroll compressor of the back pressure cavity configuration of above-described embodiment The high-pressure fluid of the compression chamber 11 of intermediate pressure and the discharge chamber 12 of high pressure is guided to orbiter 202 respectively with binary channels Back pressure side, back pressure caused by the high pressure fluid from discharge chamber 12 always can mutually support with the active force of discharge chamber 12 Disappear, back pressure caused by the intermediate pressure fluid from compression chamber 11 always can be with suction muffler 10, the active force of compression chamber 11 Cancel out each other, so as to realize under different pressure ratio working conditions, both may insure each operating mode pump housing axial seal, and avoided simultaneously There is the problem of back pressure surplus.Back pressure caused by the first back pressure and the second back pressure is so caused to make a concerted effort to fluctuate more It is small, run orbiter 202 more stable, the vibration and noise of screw compressor can be reduced.

The scroll compressor of the utility model embodiment, as shown in figure 1, its used back pressure cavity configuration is mainly in Between pressure and pressure at expulsion two back pressure chambers composition, i.e. the first back pressure chamber 13 and the second back pressure chamber 14, the first back pressure chamber 13 and the Two back pressure chambers 14 are in the annular region between support 401 and orbiter 202.It is close that floating is provided with second back pressure chamber 14 Sealing assembly 6, the first back pressure chamber 13 and the second back pressure chamber 14 are sealed against each other by isolation by floating seal assembly 6.By in end cap End cap is opened up on 502 and draws high-pressure oil gas passage 509, fixed scroll is opened up on fixed scroll 201 and draws high-pressure oil gas passage 208, Support is opened up on support 401 and draws high-pressure oil gas passage 410, three passages are sequentially communicated the second drainage channel of composition 17 will exhaust The high-pressure oil gas of the reserve 15 of the bottom of chamber 12 are guided to the second back pressure chamber 14, so as to form high pressure back pressure chamber.On the other hand, exist The first drainage channel 16 is opened up on orbiter 202, compression chamber 11 is connected with the first back pressure chamber 13, so as to form intermediate pressure Back pressure chamber.

In the second back pressure chamber 14 under the effect of high-pressure oil gas pressure, floating seal assembly 6 is promoted to be adjacent to orbiter 202 The exterior lateral area of back pressure side end face, the first back pressure chamber 13 is isolated with suction muffler 10, realize the sealing of the first back pressure chamber 13.It is middle The air pressure of pressure back pressure chamber directly acts on the central area of the driving bearing side end face of orbiter 202.So as to realize, Under different pressure ratio working conditions, there is provided suitable back pressure, both may insure each operating mode pump housing axial seal, while avoided out The problem of now back pressure is superfluous or insufficient.

In addition, the screw compressor of the present embodiment is also equipped with a kind of oil channel structures, can be in time by the storage of the bottom of discharge chamber 12 The high pressure refrigeration oil in oily area 15 imports the second back pressure chamber 14, and throttling oil supplying hole 610, control are opened up on floating seal ring 601 The throttling oil supplying hole 610 connects or the first back pressure chamber 13 connects with the revolution motion of orbiter 202 with suction muffler 10.The oil Line structure can in time by the high pressure refrigeration oil of the reserve 15 of discharge chamber 12 guiding backflow and reasonable distribution to suction muffler 10 with First back pressure chamber 13, avoid condenser or evaporator that air-conditioning system is brought a large amount of refrigeration oils into screw compressor exhaust, shadow Ring air conditioner two-unit heat exchange；Meanwhile refrigeration oil is back to suction muffler 10, the first back pressure chamber 13 in time, energy fully effectively lubricating respectively rubs Secondary, reduction frictional dissipation and abrasion are wiped, and forms the oil film needed for pump housing sealing, raising compressor performance and reliability, is kept away The problem of a large amount of refrigeration oils are pulled away and cause compressor oil starvation is exempted from.By further designing oil channel structures, can be achieved to pressure The fuel feeding of contracting chamber 11, on the premise of compressor air suction efficiency is not influenceed, ensure the sufficient lubrication of compression chamber 11 and sealing.

Screw compressor of the present utility model is described in detail with specific embodiment below in conjunction with the accompanying drawings.

As shown in figure 1, the screw compressor of the utility model embodiment, mainly includes compression mechanism 2, electric machine assembly 3, passes Dynamic drive mechanism 4, case component 5 and floating seal assembly 6.

Compression mechanism 2 includes：Fixed scroll 201, orbiter 202 and its driving bearing 203, anti-rotation steel ring 204, row Air-valve assembly 205, high-low pressure parting seal circle 206, draw high-pressure channel sealing ring 207.Fixed scroll 201 and the rigidity of support 401 It is connected on case component 5, is connected by alignment pin 409 with support 401；Orbiter 202 is driven by bent axle 402 and anti- In the presence of free-wheeling system, make around the center of fixed scroll 201 without rotation, the radius of gyration is R revolution translation.Fixed scroll 201 Scrollwork tooth is respectively provided with orbiter 202, and the scrollwork tooth of fixed scroll 201 and orbiter 202 is made up of conjugation molded line, can phase Mutually engagement forms crescent moon into compression chamber, and orbiter 202 is in the presence of transmission drive mechanism 4 with anti-rotation mechanism, compression chamber 11 are constantly elapsed to center, and volume is constantly reduced, and pressure is constantly compressed in compression chamber 11, so as to realize gas compression.

Transmission drive mechanism 4 includes support 401, bent axle 402, crank-pin 403, eccentric bushing 404, base bearing 405 and countershaft Hold 406.Support 401 is angularly positioned with fixed scroll 201 by alignment pin 409, and end face is adjacent to, and in the compression of end cap 502 With under the supporting role of housing 501, support 401 and fixed scroll 201 are fixed on case component 5.405 inside and outside circle of base bearing Respectively with bent axle 402, the elastic conjunction of support 401；The outer ring of supplementary bearing 406 and the elastic conjunction of housing 501, between inner ring and bent axle 402 Gap is assembled.In addition, crank-pin 403 assembles with the elastic conjunction of bent axle 402 in one, eccentric bushing 404 with the gap of crank-pin 403, partially Heart set 404 assembles with the gap of driving bearing 203.Therefore, bent axle 402 is under base bearing 405 and the supporting role of supplementary bearing 406, axle Limited to the free degree, can only make revolution operation.Bent axle 402 rotates, and drives crank-pin 403 to run together, so as to pass through driving Bearing 203 drives orbiter 202 and eccentric bushing 404 to operate.

Anti-rotation mechanism is made up of 6 groups of anti-rotation steel rings 204 with anti-rotation straight pin 407, the back pressure side of orbiter 202 Mounting hole is offered on end face, anti-rotation steel ring 204 is arranged in the mounting hole, the anti-force fit support of rotation straight pin 407 401, and the difference of the internal diameter of anti-rotation steel ring 204 and the anti-diameter of rotation straight pin 407 is equal to 2 times of radius of gyration R.The mechanism Equivalent to parallel four-bar linkage, wherein orbiter 202 is equivalent to connecting rod, due to belonging to parallel four-bar linkage, dynamic vortex Disk 202 makees revolution translation.

Electric machine assembly 3 is arranged in suction muffler 10, it include motor stator 301, rotor 302, main balance weight 303, Secondary balance weight 304 and rotor cover plate 305 and rotor cover plate 306.Motor stator 301 is connected with the interference of case component 5, and motor turns Son 302 is together with the assembly connection of bent axle 402, so as to which motor power is transferred into compression mechanism 2 by bent axle 402, drives dynamic whirlpool Capstan 202 makees revolution translation.Orbiter 202 is in operation process, eccentric bushing 404, main balance weight 303 and secondary balance weight 304 are used to balance the centrifugal force of orbiter 202 and its caused torque, make entirely to move revolving part and are in poised state.

Case component 5 includes：Housing 501, end cap 502, end cap 502 by fastening bolt 505 be connected on housing 501 from And form closed container.Air entry 506 is opened up on housing 501, is suction muffler 10 with 506 connected regions of air entry, group of motors Part 3 is in suction muffler 10.End is bonded with fixed scroll 201 high-low pressure parting seal circle 206 is set in end cap 502, will The exhaust side of suction muffler 10 and fixed scroll 201 separates, and so as to form discharge chamber 12, discharge chamber 12 is let out with fixed scroll 201 Pressure hole connects with central exhaust port, while is connected with the exhaust outlet 507 on end cap 502.Fixed scroll 201 and orbiter 202 Scrollwork tooth is intermeshed to form compression chamber 11.The second back pressure chamber 14 is formed between support 401 and floating seal assembly 6, and is set Passage guides high-pressure oil gas to the second back pressure chamber 14；In the junction of support 401 and bent axle 402, axle envelope 702 and jump ring are set 701 realize the sealing at the rear portion of support 401, floating seal assembly 6 and the end face gluing, sealing of orbiter 202, so as to form first Back pressure chamber 13, and open up the first drainage channel 16 on orbiter 202 and connect the first back pressure chamber 13 with compression chamber 11.Holding Lid 502 sets oil centrifugal mechanism 503, and the refrigeration oil for being vented carrying is separated by centrifugal action and accumulates in discharge chamber 12 The reserve 15 of bottom, in order to avoid refrigeration oil is carried away by exhaust again, set on end cap 502 and keep off oily rib 510, keep off oily rib 510 are extended to the position relative with central exhaust port by the top of discharge chamber 12, so as to make the exhaust of compression chamber 11 upward The oil ease-hole 508 for flowing and being kept off by being opened on oily rib 510 enters oil centrifugal mechanism 503 and finally by exhaust outlet 507 discharge compressors, exhaust and the refrigeration oil contact area in reserve 15 can be effectively reduced by keeping off oily rib 510, maximize resistance Only refrigeration oil takes compressor out of by high pressure draught.

Floating seal assembly 6 includes：Floating seal ring 601, the first sealing ring 602, the second sealing ring 603 and wear plate 604 etc..Floating seal assembly 6 be arranged at support 401 open up on annular groove and can orbiter 202 axial movement.Pass through End cap is opened up on end cap 502 to draw high-pressure oil gas passage 509, on fixed scroll 201 open up fixed scroll and draw high-pressure oil gas and lead to Road 208 and opened up on support 401 support draw high-pressure oil gas passage 410 form the second drainage channel 17, high-pressure oil gas are drawn The end face of floating seal assembly 6 is directed at, under high-pressure oil gas effect, pushes floating seal assembly 6 to orbiter 202, Liang Zheduan Face is mutually adjacent to and realizes end face seal.

In specific work process, after electric machine assembly 3 is powered, transmission drive mechanism 4 is driven to rotate, and drive dynamic vortex Disk 202 makees translation of continuously revolving round the sun, and the scrollwork tooth of orbiter 202 engages to form compression chamber 11 with the scrollwork tooth of fixed scroll 201, compression Chamber 11 is constantly elapsed to center, and volume is constantly reduced, and gas is constantly compressed in cavity；When compression reaches predetermined compression ratio Under gas pressure effect, exhaust valve component 205 is pushed open, refrigerant is arranged by the center exhaust outlet or relief hole of fixed scroll 201 Go out, into discharge chamber 12.

As shown in Figures 1 to 7, the specific work process of the screw compressor of the utility model embodiment is as follows：

After being powered to electric machine assembly 3, under the interaction in rotor magnetic field, the high-speed rotation of rotor 302, and drive Transmission drive mechanism 4 rotates, and driving orbiter 202 operates, and orbiter 202 is under anti-rotation mechanism effect, with revolution half Footpath R makees revolution translation around the center of fixed scroll 201, and the scrollwork tooth of orbiter 202 engages to form pressure with the scrollwork tooth of fixed scroll 201 Contracting chamber 11, compression chamber 11 are constantly elapsed to center, and volume is constantly reduced, and gas is constantly compressed in cavity；When compression reaches During predetermined compression ratio under gas pressure effect, push air bleeding valve or relief valve open, refrigerant by fixed scroll 201 center exhaust outlet Or relief hole discharge, into discharge chamber 12.

Under the swabbing action of compression mechanism 2, refrigerant enters from the air entry 506 being connected with air-conditioning system evaporator outlet Enter the suction muffler 10 of compressor, process simultaneously cools down electric machine assembly 3, is then drawn into orbiter 202 and the scrollwork of fixed scroll 201 Tooth is engaged in formed compression chamber 11, while partial freeze oil is also sucked into compression chamber 11 existing for suction muffler 10.With song Axle 402 rotates, and compression chamber 11 is closed and starts to compress, and gas continues back pressure contracting and reaches certain pressure, through the center of fixed scroll 201 Steam vent or relief hole enter discharge chamber 12；Refrigerant in discharge chamber 12 is in air-fuel mixture state, by end cap 502 Oil ease-hole 508 enters oil centrifugal mechanism 503 and simultaneously rotated around it, under the action of the centrifugal force, heavier mass it is cold Frozen oil mist is separated, and the reserve 15 of lower section is back to along perisporium；On the other hand, refrigerant side is through oil centrifugal mechanism 503 discharge compressor with exhaust outlet 507, subsequently into the condenser of air-conditioning system.

Accumulate in reserve 15 refrigeration oil pass through high-pressure oil gas passage 509 drawn by end cap, fixed scroll draws high-pressure oil gas The second drainage channel 17 that passage 208 and support draw the composition of high-pressure oil gas passage 410 enters by support 401 and floating seal group The region of the second back pressure chamber 14 that part 6 is formed.End cap draw filter screen 504 is provided with high-pressure oil gas passage 509 can be to passing through Refrigeration oil is filtered.High-pressure oil gas into the second back pressure chamber 14 promote floating seal assembly 6, make itself and orbiter 202 End face is close to and realizes end face seal, while provides back pressure Fdb for orbiter 202.Further, the region of the second back pressure chamber 14 Interior high pressure refrigeration oil is back to the back pressure of suction muffler 10 or first by the throttling oil supplying hole 610 set on floating seal ring 601 Room 13, and by setting throttling oil supplying hole 610 flow export position, it is controlled with the revolution motion of orbiter 202 selectivity Ground connects with suction muffler 10 or the first back pressure chamber 13 connects.The oil channel structures in time can guide the high pressure refrigeration oil of reserve 15 Flow back and reasonable distribution is to the back pressure chamber 13 of suction muffler 10 or first, avoid compressor air-discharging and bring a large amount of refrigeration oils into air-conditioning The problems such as condenser and evaporator of system, influenceing the heat exchange of the device of system two, and causing compressor oil starvation；Meanwhile refrigeration oil and When be back to suction side, back pressure cavity and compression chamber, can abundant each friction pair of effectively lubricating, reduce frictional dissipation and abrasion, and The oil film needed for pump housing sealing is formed, improves compressor performance and reliability.By further designing oil channel structures, can be achieved to work as Suction muffler starts, to the chamber fuel feeding, on the premise of compressor air suction efficiency is not influenceed, to ensure compression chamber sufficient lubrication when closing With sealing.

On the other hand, axle envelope 702 and jump ring 701 are set in support 401 and the junction of bent axle 402, and pass through floating seal Component 6 fits sealing with the end face of orbiter 202, so as to form the first back pressure chamber 13, and opens up first in orbiter 202 and draws Circulation road 16 connects the first back pressure chamber 13 with compression chamber 11.Medium pressure gas in compression chamber 11 enters by the first drainage channel 16 Enter the first back pressure chamber 13, back pressure Fmb is produced to orbiter 202 under the medium pressure gas effect of the first back pressure chamber 13.Therefore, By pressure at expulsion Pd, intermediate pressure Pmid, (there is directly pass in intermediate pressure Pmid and pressure of inspiration(Pi) Ps to the back pressure of orbiter 202 System) two back pressure chamber compositions, therefore, back pressure average pressure is Pb=KPs+ ε Pd.And the separation force such as front gas force can be with Weighed with average value P a, and there are Pa=σ Ps+ ω Pd.It is near by designing high pressure and intermediate pressure back pressure cell structure K It is similar to σ and ε is similar to ω, therefore with operating mode air-breathing Ps and pressure at expulsion Pd change, also can guarantee that back pressure average pressure Pb Approximate and just slightly larger than positive separation force average pressure Pa, it is possible to ensure each operating mode pump housing axial seal, keep away simultaneously Exempt from back pressure surplus.

The back pressure surplus Mt/Mb of the screw compressor of existing screw compressor and the present embodiment is bent with operating mode pressure ratio Line, (wherein Mt is to make the opplied moment that Moving plate topples caused by gas force, centrifugal force etc., and Mb is back pressure as shown in figure 12 The opplied moment that caused anti-arresting disc topples), the screw compressor back pressure surplus-operating mode pressure ratio curve of the present embodiment is oblique Rate is smaller.

In brief, the back pressure side chamber pressure of orbiter 202 is by pressure of inspiration(Pi) Ps, compression cavity pressure Pi and pressure at expulsion Pd is formed, and wherein Pi is determined by compressor arrangement and Ps, and independent condition parameter is Ps and Pd；The back pressure of the utility model embodiment Cavity configuration is made up of ridge of high pressure pressure Pd and middle pressure back pressure cavity Pi two parts, and ridge of high pressure pressure Pd is the second back pressure chamber 14, middle pressure Back pressure cavity Pi is the first back pressure chamber 13 so that back pressure independent parameter is also Ps and Pd, as long as rationally designing back pressure cavity area, is made Back pressure is appropriate and optimizes the accounting of distribution high pressure back pressure and middle pressure back pressure, can realize the effect above.It will be understood that For, back pressure Fdb caused by the second set back pressure chamber 14 always can approximate and discharge chamber 12 active force cancel out each other； Back pressure Fmb caused by the first set back pressure chamber 13 always can the approximate active force phase with suction muffler 10, compression chamber 11 Mutually offset, so can both may insure each operating mode pump housing axial seal to realize under different pressure ratio working conditions, and kept away simultaneously Exempt from the problem of back pressure surplus occur.

On the other hand, because the second back pressure chamber 14 connects with discharge chamber 12 always so that what the second back pressure chamber 14 was produced Back pressure substantially constant；First back pressure chamber 13 only needs to connect with compression chamber 11, it is not necessary to connected with discharge chamber 12, avoid because with Orbiter 202 revolves round the sun, and the first back pressure chamber 13 with compression chamber 11 by connecting the pressure transitted to caused by being connected with discharge chamber 12 Mutation, reduces the pressure oscillation in the first back pressure chamber 13.So so that produced by the second back pressure chamber 14 and the first back pressure chamber 13 Back pressure make a concerted effort fluctuate it is smaller, run orbiter 202 more stable, vibration of compressor and noise can be reduced.

On the basis of above-described embodiment, as shown in Figure 8, it is preferable that compression chamber oil supply gallery is opened up on orbiter 202 19 compression chamber oil supply galleries 19 are corresponding with the throttling oil supplying hole 610 on floating seal ring 601, by controlling compression chamber oil supply gallery 19 open up position on orbiter 202, and compression chamber oil supply gallery 19 and throttling are made when compression chamber 11 enters compressive state Oil supplying hole 610 connects, and starts, to the fuel feeding of compression chamber 11, do not influenceing to press when compression chamber 11 is in compressive state so as to realize On the premise of contracting machine gettering efficiency, ensure the sufficient lubrication of compression chamber 11 and sealing.

In addition, as shown in Figure 9 and Figure 10, in order to carry out current limliting to throttling oil supplying hole 610, floating seal ring 601 is divided into Two parts, and two parts are bolted integrally, section is set in the throttling oil supplying hole 610 between two parts Ductility limit pressure valve 607 carries out current limliting to throttling oil supplying hole 610, and floating seal ring 601 uses Split assembled structure, is easy to set throttling Pressure limiting valve 607.

As shown in figure 11, further improved on the basis of above-described embodiment, the 3rd drainage channel is opened up in support 401 18, and the first unidirectional stop valve 606 is set in the 3rd drainage channel 18, the second back pressure chamber 14 is to cut to the first back pressure chamber 13 Only direction；Second unidirectional stop valve 605 is set in the second drainage channel 17, prevents from returning from the second back pressure chamber 14 to discharge chamber 12 Stream.For not setting relief valve in compression chamber 11 or having set relief valve to fail timely and effective pressure release, compressor easily occurred During compression, the pressure of the first back pressure chamber 13 can be caused to be higher than the pressure of the second back pressure chamber 14, now the first unidirectional stop valve 606 and the Two unidirectional stop valves 605 work, and the second back pressure chamber 14 connects with than being vented the first higher back pressure chamber 13, and and discharge chamber 12 unidirectional cutoffs.So as to increase gas pressure in the second back pressure chamber 14, so as to ensure the pump housing axle in the case where there is overcompression To effective sealing.

As shown in figure 12, back pressure cavity configuration used by the utility model, mainly by intermediate pressure and pressure at expulsion two Back pressure chamber forms, i.e. the first back pressure chamber 13 and the second back pressure chamber 14, therefore, back pressure average pressure is Pb=KPs+ ε Pd；It is and positive The separation forces such as gas force can be weighed with average value P a, and have Pa=σ Ps+ ω Pd.By design intermediate pressure and Two back pressure cell structures of pressure at expulsion make it that K is similar to σ and ε is similar to ω, therefore, with operating mode air-breathing Ps and pressure at expulsion Pd Change, also can guarantee that back pressure average pressure Pb is approximate and just slightly larger than positive separation force average pressure Pa, it is possible to Ensure each operating mode pump housing axial seal, while avoid back pressure superfluous.

Preferred embodiment of the present utility model is the foregoing is only, is not limited to the utility model, for this For the technical staff in field, the utility model can have various modifications and variations.It is all in the spirit and principles of the utility model Within, any modification, equivalent substitution and improvements made etc., it should be included within the scope of protection of the utility model.

Claims (22)

1. a kind of back pressure cavity configuration, it is characterised in that the back pressure cavity configuration includes：

First back pressure chamber (13), the firstth area being arranged between the orbiter (202) of screw compressor (1) and support (401) Domain；

First drainage channel (16), the first end of first drainage channel (16) and the compression chamber of the screw compressor (1) (11) connect, the second end of first drainage channel (16) extends to first back pressure chamber (13) so as to come from the compression The fluid of chamber (11) applies the first back pressure by first back pressure chamber (13) to the orbiter (202)；

Second back pressure chamber (14), the second area being arranged between the orbiter (202) and the support (401)；

Second drainage channel (17), the first end of second drainage channel (17) and the discharge chamber of the screw compressor (1) (12) connect, the second end of second drainage channel (17) extends to second back pressure chamber (14) so as to come from the exhaust The fluid of chamber (12) applies the second back pressure by second back pressure chamber (14) to the orbiter (202)；

Wherein, the first area and the second area are spaced different zones, along the orbiter (202) Radially, the first area is located at the inner side of the second area.

2. back pressure cavity configuration according to claim 1, it is characterised in that the support (401) includes：

Master body (413)；

First annular flange (411), the end face of the master body (413) is arranged on along the circumferentially extending of the master body (413) On, and protrude and set towards the orbiter (202)；

Wherein, the first area is the master body (413), the first annular flange (411) and the orbiter (202) annular compartment enclosed.

3. back pressure cavity configuration according to claim 2, it is characterised in that the support (401) also includes：

Second annular flange (412), the master body (413) is extended on around the periphery of the first annular flange (411) End face on, and towards the orbiter (202) protrude set；

Wherein, the second area is the master body (413), the first annular flange (411), second annular flange And the annular compartment that encloses of the orbiter (202) (412).

4. according to the back pressure cavity configuration described in any one of claim 1 or 3, it is characterised in that the back pressure cavity configuration also includes：

Floating seal assembly (6), second back pressure chamber (14) is arranged on being axially moveable work along the orbiter (202) It is interior, second back pressure chamber (14) is sealed；

The floating seal assembly (6) is the pressure effect of the fluid from the discharge chamber (12) is lower and the orbiter (202) at least part aft bulkhead is abutted to apply second back pressure and by described first to the orbiter (202) Suction muffler (10) isolating seal of back pressure chamber (13) and the screw compressor (1).

5. back pressure cavity configuration according to claim 4, it is characterised in that the floating seal assembly (6) includes：

Floating seal ring (601), second back pressure chamber (14) is arranged on being axially moveable work along the orbiter (202) It is interior to apply second back pressure to the orbiter (202), the first end face of the floating seal ring (601) with it is described At least part aft bulkhead of orbiter (202) abuts, second end face and the support of the floating seal ring (601) (401) it is relative；

Wherein, the first end face and the second end face are two relative end faces of the floating seal ring.

6. back pressure cavity configuration according to claim 5, it is characterised in that the floating seal assembly (6) also includes：

Wear plate (604), it is folded in the first end face of the floating seal ring (601) with the orbiter (202) at least With by suction muffler (10) isolating seal of first back pressure chamber (13) and the screw compressor (1) between portion rear end wall.

7. back pressure cavity configuration according to claim 6, it is characterised in that along the inner ring of the floating seal ring (601) The first seal groove (608) is circumferentially offered, the first sealing ring (602) is arranged with first seal groove (608) with by described in Second back pressure chamber (14) seals.

8. back pressure cavity configuration according to claim 7, it is characterised in that along the outer ring of the floating seal ring (601) The second seal groove (609) is circumferentially offered, the second sealing ring (603) is arranged with second seal groove (609) with by described in Second back pressure chamber (14) seals.

9. back pressure cavity configuration according to claim 8, it is characterised in that first seal groove (608) and described second Seal groove (609) is to be opened in recessed groove of the floating seal ring (601) along its axial middle part or be opened in described The step groove of the second end face of floating seal ring (601).

10. the back pressure cavity configuration according to any one of claim 5 to 9, it is characterised in that the floating seal ring (601) With offer flow-guiding channel on the orbiter (202), the fluid in second back pressure chamber (14) is through the flow-guiding channel Flow into first back pressure chamber (13), or flow into the compression chamber (11) through the flow-guiding channel or the suction muffler (10) in.

11. back pressure cavity configuration according to claim 10, it is characterised in that the flow-guiding channel includes being opened in described float Throttling oil supplying hole (610) on rotary packing ring (601), axle of the throttling oil supplying hole (610) along the floating seal ring (601) To extension, to connect the first end face of the floating seal ring (601) and the second end face.

12. back pressure cavity configuration according to claim 11, it is characterised in that the flow-guiding channel is also described including being opened in Guiding gutter on orbiter (202), the guiding gutter are arranged on the aft bulkhead of the orbiter (202) and are used for Connected with the throttling oil supplying hole (610).

13. back pressure cavity configuration according to claim 12, it is characterised in that the orbiter (202) have relative to The fixed scroll (201) of the screw compressor (1) mobile first position and the second place；

When the orbiter (202) is moved to the first position, it is described throttling oil supplying hole (610) by the guiding gutter with First back pressure chamber (13) connection；When the orbiter (202) is moved to the second place, the throttling oil supplying hole (610) connected with the compression chamber (11) or the suction muffler (10)；

Wherein, when the orbiter (202) is moved to the first position, the compression chamber (11) and the suction muffler (10) Cut-off is so that the compression chamber (11) is in compressive state；It is described when the orbiter (202) is moved to the second place Compression chamber (11) connects with the suction muffler (10) so that the compression chamber (11) is in suction condition.

14. back pressure cavity configuration according to claim 13, it is characterised in that offered on the orbiter (202) with The compression chamber oil supply gallery (19) of compression chamber (11) connection；

When the orbiter (202) is moved to the first position, the compression chamber oil supply gallery (19) and throttling oil supplying hole (610) connect so that the fluid in second back pressure chamber is led to by the throttling oil supplying hole (610) and the compression chamber fuel feeding Road (19) flows into the compression chamber (11).

15. the back pressure cavity configuration according to any one of claim 11 to 14, it is characterised in that the floating seal assembly (6) also include：

Throttle pressure limiting valve (607), is arranged in the throttling oil supplying hole (610), for flowing through the throttling oil supplying hole (610) Fluid throttled and be depressured；

Wherein, the entrance point of throttling pressure limiting valve (607) is set towards second back pressure chamber (14), to prevent the throttling fuel feeding Reverse flow of fluids in hole (610) is returned in second back pressure chamber (14).

16. back pressure cavity configuration according to claim 15, it is characterised in that the floating seal ring (601) includes：

First ring body (611) and the second ring body (612), first ring body (611) and second ring body (612) are removably Connection；

Wherein, offered on the end face that second ring body (612) is used to be connected with first ring body (611) along the throttling The positioning hole (613) of the axis extension of oil supplying hole (610), the throttling pressure limiting valve (607) are arranged on the positioning hole (613) It is interior.

17. back pressure cavity configuration according to claim 1, it is characterised in that the back pressure cavity configuration also includes：

3rd drainage channel (18), one end of the 3rd drainage channel (18) connects with first back pressure chamber (13), described The other end of 3rd drainage channel (18) connects with second back pressure chamber (14), by the stream in first back pressure chamber (13) Body is drained in second back pressure chamber (14).

18. back pressure cavity configuration according to claim 17, it is characterised in that the back pressure cavity configuration also includes：

First unidirectional stop valve (606), first unidirectional stop valve (606) are arranged in the 3rd drainage channel (18), The entrance point of first unidirectional stop valve (606) is set towards first back pressure chamber (13), so that the 3rd drainage is logical Road (18) is from first back pressure chamber (13) to the second back pressure chamber (14) one-way conduction.

19. back pressure cavity configuration according to claim 17, it is characterised in that the back pressure cavity configuration also includes：

Second unidirectional stop valve (605), second unidirectional stop valve (605) are arranged in second drainage channel (17), The entrance point of second unidirectional stop valve (605) is set towards the discharge chamber (12), so that second drainage channel (17) from the discharge chamber (12) to the second back pressure chamber (14) one-way conduction.

20. back pressure cavity configuration according to claim 1, it is characterised in that the bottom of the discharge chamber (12) has oil storage Area (15), the first end of second drainage channel (17) connect with the reserve (15).

21. back pressure cavity configuration according to claim 1, it is characterised in that first drainage channel (16) is moved along described The axial direction of scroll plate (202) is opened on the orbiter (202).

22. a kind of scroll compressor, including back pressure cavity configuration, it is characterised in that the back pressure cavity configuration will for aforesaid right Seek the back pressure cavity configuration any one of 1 to 21.