CN205823629U - Scroll compressor having a plurality of scroll members - Google Patents
Scroll compressor having a plurality of scroll members Download PDFInfo
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- CN205823629U CN205823629U CN201620544751.4U CN201620544751U CN205823629U CN 205823629 U CN205823629 U CN 205823629U CN 201620544751 U CN201620544751 U CN 201620544751U CN 205823629 U CN205823629 U CN 205823629U
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- Prior art keywords
- dynamic
- stop part
- scroll element
- vortex
- stop
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Abstract
The utility model provides a scroll compressor, include: the fixed scroll component comprises a fixed scroll end plate and a fixed scroll blade; the movable vortex component comprises a movable vortex end plate, a movable vortex blade and a hub; a main bearing housing supporting the orbiting scroll member and having a recess for receiving a boss of the orbiting scroll member; and the stopping structure is configured to stop the movable scroll part during the movement of the movable scroll part so as to reduce or prevent the collision between the fixed scroll blade and the movable scroll blade. The utility model discloses alleviate effectively or avoided the motion process of moving vortex part decide the vortex blade and move the collision between the vortex blade to alleviate or avoided the damage of blade, reduced the risk that the vortex topples, improved scroll compressor's performance and reliability.
Description
Technical field
This utility model relates to a kind of screw compressor.
Background technology
The content of this part provide only the background information relevant to the disclosure, and it may be not intended that prior art.
Screw compressor generally includes housing, accommodates compression mechanism in the housing, rotary shaft, drive mechanism, base bearing
Seat etc..Wherein, compression mechanism includes determining scroll element and dynamic scroll element.Drive mechanism includes stator and rotor.Determine vortex
Parts are fixing in the housing, and dynamic scroll element is supported in the housing by main bearing seat.Rotary shaft is through rotor and at rotor
Drive lower rotation.Generally, one end of rotary shaft being provided with eccentric crank pin, eccentric crank pin stretches into the hub portion of dynamic scroll element
In, thus, in the rotary course of rotary shaft, it is further driven to dynamic scroll element action by eccentric crank pin.
Due to the eccentric setting of eccentric crank pin, in the running of screw compressor, move scroll element and determine vortex
Easily collide between the blade of parts, particularly all the more so in the case of the middle and high speed of screw compressor is run.Blade
Between collision not only easily cause the friction damage of blade, but also can exceed that the limit of the material of scroll element causes blade
Rupture.Additionally, the collision aggravation when screw compressor high-speed cruising, between blade so that the tilting moment of dynamic scroll element
Increase, thus cause dynamic scroll element to topple, these performances that the most greatly have impact on screw compressor and operation can
By property.
The development of technology is more and more higher to the rotation speed requirements of screw compressor, and existing screw compressor is running up
In the case of collision serious between blade also become and limit the principal element that screw compressor rotating speed promotes.Therefore, for ability
For the technical staff in territory, urgent problem is to provide the screw compressor of a kind of improvement, with alleviate or avoid blade it
Between collision, the risk reducing or avoiding vortex to topple, and for screw compressor speed-raising improve provide strong structure prop up
Support.
Utility model content
A purpose of the present utility model is to provide a kind of screw compressor, to alleviate or to avoid dynamic volution blade with fixed
Collision between volution blade, and then alleviate or avoid the blade rubbing caused because of blade collision damage or rupture.
Another purpose of the present utility model is to provide a kind of screw compressor, to reduce the tilting moment of vortex, reduces
The risk that vortex topples.
Another purpose of the present utility model is to provide a kind of screw compressor, to improve the performance of screw compressor, carries
High screw compressor reliability of operation.
Further object of the present utility model is to provide a kind of screw compressor, to adapt in market carry screw compressor
The demand of speed, for the technical support that the speed-raising offer of screw compressor is strong.
An aspect according to this utility model embodiment, it provides a kind of screw compressor, including: determine scroll portion
Part, described determine scroll element include determining vortex end plate and be formed at described determine vortex end plate side determine volution blade；Dynamic vortex
Parts, described dynamic scroll element includes dynamic vortex end plate, the dynamic volution blade being formed at described dynamic vortex end plate side and formation
Hub portion at described dynamic vortex end plate opposite side；Main bearing seat, described main bearing seat supports described dynamic scroll element and has use
Recess in the described hub portion receiving described dynamic scroll element；And stop configurations, described stop configurations is configured to described
Described dynamic scroll element is carried out by the motor process of dynamic scroll element backstop with alleviate or prevent described determine volution blade and
Collision between described dynamic volution blade.Owing to being provided with described stop configurations, alleviate or prevent the fortune of dynamic scroll element
The collision between volution blade and dynamic volution blade is determined such that it is able to alleviate or avoid the friction between blade to damage during Dong
Bad, it is possible to alleviate or avoid rupturing of blade, be conducive to extending the service life of screw compressor.
According to an embodiment, described stop configurations is the first backstop of the periphery being arranged in described dynamic vortex end plate
Part, with by the backstop of the described dynamic vortex end plate of described dynamic scroll element motion in a radially outer direction is alleviated or
Prevent the described collision determining volution blade and described dynamic volution blade.In the present embodiment, by the first stop part to dynamic whirlpool
The radially outer motion of rotation end plate carries out backstop, and then the radial outward movement of dynamic scroll element is carried out backstop, thus subtracts
Light or anti-stop volution blade and the collision determined between volution blade.In this case, owing to determining scroll element and dynamic whirlpool
Radially contacting with between rotation parts has a little been moved down on the first stop part and dynamic vortex end plate by blade.It therefore reduces apply
The arm of force of the active force on dynamic scroll element, the tilting moment of vortex reduces, and the risk that vortex topples also reduces, and has
It is beneficial to improve screw compressor reliability of operation.
According to an embodiment, described first stop part has interior stop surface, the radius R of described interior stop surface1It is equal to
Or it is slightly less than the radius R of the described dynamic vortex end plate of described dynamic scroll elementOSBoth offset E with described dynamic scroll element
Sum.So, in the motor process of dynamic scroll element, by contacting between the first stop part with dynamic vortex end plate,
Can effectively alleviate or prevent the collision between blade, and then the collision between can alleviating or avoid because of blade causes
Blade wear and fracture.
According to an embodiment, described first stop part is arranged on described to be determined on vortex end plate.By suitably adjusting
Determine the structure of vortex end plate, this first stop part can be realized relatively easily.
According to an embodiment, described first stop part is to determine lateral along dynamic vortex end plate of vortex end plate from described
Extend and formed determine vortex skirt section.It is to say, the first stop part forms with determining vortex end plate.Integral structure is just
In processing and fabricating, and reliability is higher.Optionally, the first stop part can also be single parts and pass through suitably
Connected mode be fixedly connected to determine vortex end plate.
According to an embodiment, described first stop part is arranged on described main bearing seat.Similarly, by suitably
Adjust the structure of main bearing seat, this first stop part can be realized relatively easily.
According to an embodiment, described first stop part is from lateral along described dynamic vortex end plate of described main bearing seat
The main bearing seat skirt section extended and formed.Similarly, integral structure is easy to processing and fabricating, and reliability is higher.Additionally, the
One stop part can also be for being fixedly connected to the additional parts of main bearing seat.
According to an embodiment, described stop configurations is be arranged in the female portion of described main bearing seat second
Stop part, alleviating by the motion radially outward direction of the described hub portion of described dynamic scroll element being carried out backstop or
Person prevents the described collision determining volution blade and described dynamic volution blade.In this embodiment, by dynamic scroll element
The backstop of the radially outer motion in hub portion, realizes the backstop of radial outward movement to whole dynamic scroll element, and then subtracts
Light or anti-stop volution blade and the collision determined between volution blade.
According to an embodiment, described second stop part is arranged in described hub portion, and described second stop part
The radius R of outer stop surface2With the offset of described dynamic scroll element E's and the most described main bearing seat described in
The radius R of recessR.So, in the motor process of dynamic scroll element, by the recess of main bearing seat to the second stop part
The backstop of motion so that achieve the backstop of radial outward movement to dynamic scroll element, effectively alleviate or avoid leaf
Collision between sheet, thus alleviate or avoid the abrasion of blade or rupture.
Alternatively, described second stop part is formed on the outer surface in described hub portion, or, described second backstop
Part is fixedly connected to the described outer surface in described hub portion.
Alternatively, described second stop part is arranged at the medium position in described hub portion, or described second stop part edge
The whole outer surface in described hub portion and extend, or described second stop part includes being axially spaced cloth along described hub portion
Multiple second stop parts put.Second stop part is arranged at the medium position in hub portion or along hub portion the most equably
Arrange, be conducive to the easy motion of dynamic scroll element, improve the stability of screw compressor.
According to an embodiment, described second stop part is arranged on the medial wall in the female portion of described main bearing seat
On, and the radius R of the interior stop surface of described second stop part3It is equal to or slightly less than the described hub portion of described dynamic scroll element
Radius RHWith described dynamic scroll element both offset E's and.So that in the motor process of dynamic scroll element, logical
Cross the backstop to the motion in the hub portion of dynamic scroll element of the second stop part on recess, effectively alleviate or avoid blade it
Between collision, reduce the risk of blade damage and risk that vortex topples, improve life-span and the scroll compression of blade
The reliability and stability of machine.
Alternatively, described second stop part is formed on the described medial wall in the female portion of described main bearing seat
On, or described second stop part is fixedly connected to the described medial wall in the female portion.
Alternatively, described second stop part is arranged at the medium position in the female portion, or described second stop part
Extend along the whole inner surface in the female portion, or described second stop part includes along between the axial direction in the female portion
Multiple second stop parts arranged every ground.Similarly, the second stop part is arranged at the medium position in hub portion or along hub
Portion axially arranges equably, is conducive to the easy motion of dynamic scroll element, improves the kinetic stability of screw compressor.
Accompanying drawing explanation
By description referring to the drawings, the feature and advantage of one or several embodiment of the present utility model will become
Obtain easier to understand.Accompanying drawing as described herein is only in order at illustration purpose and is not intended to limit by any way this practicality
Novel scope, accompanying drawing is not necessarily drawn to scale, and some features may be exaggerated or minimized to show the thin of particular elements
Joint.In the accompanying drawings:
Fig. 1 shows the structural representation of the screw compressor according to an embodiment of the present utility model；
Fig. 2 shows the relation sketch determining between scroll element and dynamic scroll element in existing screw compressor；
Fig. 3 is the partial structurtes signal of the screw compressor according to an embodiment of the present utility model shown in Fig. 1
Figure；
Fig. 4 shows the partial structurtes schematic diagram of the screw compressor according to another embodiment of the present utility model；
Fig. 5 shows the partial structurtes schematic diagram of the screw compressor according to further embodiment of the present utility model；
Fig. 6 is the sketch determining scroll element and dynamic scroll element in Fig. 3 illustrated embodiment；
Fig. 7 is to determine scroll element, dynamic scroll element and the structure diagram of main bearing seat in Fig. 4 illustrated embodiment；
Fig. 8 shows the stress schematic diagram of the dynamic scroll element in the existing scroll compressor structure shown in Fig. 2；
Fig. 9 show as shown in Figure 3 and Figure 4 according to the dynamic scroll element in scroll compressor structure of the present utility model
Stress schematic diagram；And
Figure 10 and Figure 11 respectively illustrates dynamic scroll element and the basis as shown in Figure 3 of prior art illustrated in fig. 2
The total tilting force F being subject on the dynamic volution blade of dynamic scroll element of the present utility modelflank' and FflankAnd dynamic scroll portion
Heeling moment M on parttilting' and MtiltingComparison diagram.
Detailed description of the invention
The description of embodiment each to this utility model below is merely exemplary, and be definitely not this utility model and
Its application or restriction of usage.Use in various figures identical reference to indicate identical parts, thus like portion
The structure of part will not be repeated again.
First, with reference to Fig. 1, the operation principle of screw compressor is carried out brief description.
Fig. 1 shows the longitudinal section of the screw compressor according to an embodiment of the present utility model.Such as Fig. 1 institute
State, screw compressor generally comprise housing 110, the top cover 112 being arranged on housing 110 one end and be arranged on housing 110 another
The bottom 114 of end.In the example shown in fig. 1, the top of screw compressor is provided with for sucking fluid (such as cold-producing medium)
Inlet suction port 118, is provided with the exhaust joint 119 of the fluid after discharging compression on the housing 110 of screw compressor.Shell
Body 110 is provided with the drive mechanism 120 being made up of stator 122 and rotor 124.Screw compressor is additionally provided with drive shaft 130,
Drive shaft 130 extend through rotor 124 with by the driving of rotor 124 so that drive by determining scroll element 150 and dynamic scroll portion
The compression mechanism that part 160 is constituted.Dynamic scroll element 160 includes dynamic vortex end plate 164, is formed at dynamic vortex end plate 164 side
Hub portion 162 and the spiral helicine dynamic volution blade 166 being formed at dynamic vortex end plate 164 opposite side.Determine scroll element 150 to include determining
Vortex end plate 154, it is formed at and determines vortex end plate side spiral helicine and determine volution blade 156 and be formed at and determine the big of vortex end plate
Cause the air vent 152 of central position.
Dynamic scroll element 160 is supported by main bearing seat 140 in its side being provided with hub portion 162.Shape in main bearing seat
Become to have recess 146, hub portion 162 to be received within recess 146.One end of drive shaft 130 is by being arranged in main bearing seat 140
Base bearing 144 support.The end of this one end supported by base bearing 144 of drive shaft 130 is provided with eccentric crank pin 132.
By the driving of drive mechanism 120, drive is moved scroll element 160 relative to determining scroll element 150 translation rotation by drive shaft 130
(that is, the central axis moving scroll element 160 rotates around the central axis determining scroll element 150, but dynamic scroll element 160
Body will not rotate around the central axis of self) to realize the compression of fluid.Above-mentioned translation rotation is by determining scroll element 150 and moving
The cross slip-ring (not shown) arranged between scroll element 160 realizes.During the translation rotation of dynamic scroll element 160,
Determine scroll element 150 determine can be formed between volution blade 156 and the dynamic volution blade 166 of dynamic scroll element 160 a series of
Compression chamber.The fluid sucked via inlet suction port 118 becomes gases at high pressure after compressing in each compression chamber, these gases at high pressure
It is discharged in the inner chamber of compressor by air vent 152, and is discharged to outside screw compressor via exhaust joint 119 subsequently
Portion.
In the screw compressor example shown in Fig. 1, in the bias in the hub portion 162 of dynamic scroll element 160 with rotary shaft 130
Unloading lining 142 can also be set between crank-pin 132.In the running of screw compressor, due to eccentric crank pin 132
Being eccentric setting relative to the rotation axis of rotary shaft 130, dynamic scroll element 160 is main by self during translation rotation
The centrifugal force that produces, from the driving force component of drive shaft 130 and the effect of power of unloading lining 142 so that dynamic scroll portion
The dynamic volution blade 166 of part 160 and determine scroll element 150 determine to produce between volution blade 156 radial sealing force, thus in whirlpool
In the running of rotation compressor, determining to be formed between volution blade 156 and dynamic scroll element 160 a series of compression chamber, it is achieved
Compression to the fluid entering compression chamber.
Fig. 2 shows the relation letter determining between scroll element 150 ' and dynamic scroll element 160 ' in existing screw compressor
Figure.Screw compressor shown in Fig. 2 is generally provided with unloading lining (not between hub portion and the eccentric crank pin of dynamic scroll element
Diagram).From fig. 2 it can be seen that arrange according to the structure of this screw compressor, in the running of screw compressor, dynamic
Volution blade with determine volution blade and remain contact condition under the effect of radial force.That is, move scroll element 160 ' and determine whirlpool
Between rotation parts 150 ' contact point radially be dynamic volution blade with determine on volution blade, as shown in the P point in Fig. 2
Go out.Due to dynamic volution blade with determine volution blade during the whole service of screw compressor, be in contact condition all the time,
Therefore, this structure ensure that dynamic volution blade and determines sealing effectiveness fabulous between volution blade.But, due to dynamic vortex
Parts are relative to determining the eccentric setting of scroll element, and in the running of screw compressor, the blade of dynamic scroll element is with fixed
There is bigger radial force between the blade of scroll element, two blades are closely contacted under the effect of bigger radial force.
But, the close contact between two blades also brings along adverse influence: along with the raising of screw compressor running speed, dynamic
The radial force that volution blade undertakes increases the most therewith, and excessive radial force, in addition to the friction loss being easily caused blade, also may be used
Can exceed that the limit of the material of scroll element causes broken vane.Additionally, excessive radial force is also easy to cause toppling of vortex
Moment increases so that vortex topples, and then affects performance and the reliability of operation of screw compressor.Therefore, in practice,
For alleviating dynamic volution blade and determine damage that volution blade causes because of contact-impact therebetween and the phenomenon that vortex topples, general
Within the rotating speed of this type of screw compressor is also limited in certain velocity interval.Therefore, the screw compressor of this structure is difficult to
Meet the high-revolving requirement to screw compressor on market.
In not shown another form of scroll compressor structure, inclined in the hub portion of dynamic scroll element and rotary shaft
Unloading lining is not assembled between heart crank-pin.The screw compressor of this kind of version in, under the conditions of low cruise, dynamic whirlpool
Vane sheet and determine typically will not directly contact between volution blade, therefore, is not susceptible to the phenomenon of blade damaged in collision.But,
When the rotating speed of screw compressor improves, eccentric crank pin easily bends change under the bigger centrifugal action of dynamic scroll element
Shape, so that dynamic volution blade easily collides with determining volution blade.This equally exists and causes blade damage and vortex to topple
Risk.Therefore, such scroll compressor structure is also not suitable for running at high speed.
In order to meet the demand of the rotating speed improving screw compressor in technology evolution, this utility model people proposes one
Kind of the scroll compressor structure improved, its by arrange a kind of for alleviate or anti-stop volution blade with determine volution blade it
Between the stop configurations of collision, alleviate or anti-stop volution blade and determine the volution blade running at screw compressor
In collision, thus alleviate or avoid the damaged in collision of blade, reduce the risk that vortex topples, improve the fortune of screw compressor
Line stabilization and reliability, and the speed returning screw compressor provides the biggest space.
The most just combine Fig. 3-Figure 11 and be detailed Jie to according to the example arrangement of screw compressor of the present utility model
Continue.
According to an aspect of the present utility model, stop configurations can be and determine scroll element 150 or main bearing seat 140
It is coaxially disposed in the first stop part of the periphery of dynamic vortex end plate 164 (with reference to determining in vortex skirt section 153 and Fig. 4 in Fig. 3
Main bearing seat skirt section 143).This first stop part only has in contacting with the dynamic vortex end plate 164 of dynamic scroll element 160
Block face.This interior stop surface during the translation rotation of dynamic scroll element 160 all the time with the dynamic vortex end plate of dynamic scroll element 160
164 keep contact conditions (that is, dynamic vortex end plate 164 is the state of linear contact lay along the periphery of interior stop surface), thus pass through
The backstop of dynamic vortex end plate 164 motion in a radially outer direction is alleviated or anti-fastening volution blade by described interior stop surface
Collision between 156 and dynamic volution blade 166.That is, radially contacting with between scroll element 150 and dynamic scroll element 160 will be determined
Point is transferred to dynamic contacting between vortex end plate 164 and the interior stop surface of the first stop part by blade contact.So, at dynamic vortex
Can effectively alleviate during the translation rotation of parts 160 or avoid determining between volution blade 156 and dynamic volution blade 166
Collision, thus the damage of blade that the frictional impact between alleviating or avoiding due to blade causes, improve scroll compression
The life-span of contracting machine and reliability of operation.
It is understood that in order to the eccentric motion of dynamic scroll element being carried out effective backstop to alleviate or anti-stop
Volution blade and the collision determined between volution blade, advantageously, the radius R of the interior stop surface of the first stop part1Can equal to or
Person is slightly less than the radius R of dynamic vortex end plate 164OSSummation (that is, the R obtained after being added with the offset E of dynamic scroll element 160OS+
E).It is understood that the radius R of the interior stop surface at the first stop part1Radius R equal to dynamic vortex end plate 164OSWith dynamic whirlpool
Summation (that is, the R that the offset E of rotation parts 160 obtains after being addedOS+ E) in the case of, in the motor process of dynamic scroll element,
Move volution blade and determine may just contact or contact slightly between volution blade.While it is true, due to the first stop part
The interior stop surface backstop to the radial outward movement of dynamic vortex end plate, still be able to be effectively prevented from or alleviate two blades it
Between collision.Further, it is to be appreciated that owing to the first stop part is arranged on the periphery of dynamic vortex end plate, and it also requires protect
The eccentric motion of the dynamic vortex end plate of card, therefore, the radius R of interior stop surface1Should be greater than the radius of dynamic vortex end plate.But, vortex
The dynamic volution blade of compressor and determine to also need between volution blade form effective sealing with to the fluid entered in compression chamber
Effectively compressing, therefore, the radius of interior stop surface is arranged to be slightly less than the radius of dynamic vortex end plate and dynamic scroll element
The sum of offset, so that moving volution blade and determining to form effective sealing between volution blade.In this case, by
One stop part backstop to the radial outward movement of the dynamic vortex end plate 164 of dynamic scroll element 160 so that dynamic volution blade 166
With determine between volution blade 156, not contact (that is, there is the predetermined working clearance).Therefore, no matter screw compressor rotating speed
Change, moves volution blade 166 and determines all without colliding between volution blade 156, thus efficiently avoid rubbing of blade
Wear bad, improve the service life of blade.
Fig. 3 shows the partial structurtes schematic diagram of the screw compressor according to an embodiment of the present utility model.?
In example shown in Fig. 3, the first stop part is arranged on to be determined on vortex end plate 154.Specifically, the first stop part is formed as making whirlpool by oneself
Rotation end plate 154 formed along dynamic extending laterally of vortex end plate 164 (more specifically non-orbiting scroll end plate 154 towards dynamic
The radial outside of the first end face 1541 of vortex end plate 164 is extended this first end face 1541 and is formed) determine vortex skirt section
153.This is determined vortex skirt section 153 and is looped around the periphery of dynamic vortex end plate 164.Determine the inner peripheral surface 1531 in vortex skirt section 153 as front
The interior stop surface stated.Can have a clearer understanding of in conjunction with Fig. 6, in this example, determine the radius of the inner peripheral surface in vortex skirt section 153
R1, the radius R of dynamic vortex end plate 164OS, and the offset E of dynamic scroll element 160 between there is following relation: R1It is slightly less than
(ROS+E).Therefore, during the translation rotation of dynamic scroll element 160, dynamic vortex end plate 164 all the time with determine vortex skirt section 153
Inner peripheral surface 1531 keep contact condition, but, determine between volution blade 156 and dynamic volution blade 166 not in contact with, but tool
There is the predetermined working clearance.
In the example depicted in fig. 3, the first stop part forms with determining scroll element 150.Optionally, first only
Block piece can be independent parts and can (such as, groove mates with flange by the way of existing feasible fixing connection
Structure, screw connection structure, bonding etc.) it is fixedly connected to determine determining vortex end plate 154 or being connected to shell of scroll element 150
Body 110.
Fig. 4 shows the partial structurtes schematic diagram of the screw compressor according to another embodiment of the present utility model.
Fig. 4 illustrated embodiment differs only in Fig. 3 illustrated embodiment, in embodiment as shown in Figure 4, and the first backstop
Part is arranged on main bearing seat 140.Specifically, the first stop part can be formed as from main bearing seat 140 along dynamic vortex end plate
164 extend laterally and formed (in particular from the footpath of the first end face 141 of the racking scroll element 160 of main bearing seat 140
Be extended this first end face 141 laterally and formed) main bearing seat skirt section 143.That is, the first stop part and main bearing seat
140 form, and are looped around the periphery of dynamic vortex end plate 164.
Similarly, the first stop part can also be by existing feasible fixing connected mode (such as, groove and flange
Distribution structure, screw connection structure, bonding etc.) it is fixedly connected to the single parts of main bearing seat 140.This kind of structure is only arranged
Need the structure of main bearing seat is adjusted correspondingly.Simple in construction, cost is relatively low.
Fig. 6 and Fig. 7 is respectively the sketch of Fig. 3 and Fig. 4 example shown.Can be clear that from Fig. 6, according to this embodiment party
Formula, during the translation rotation of dynamic scroll element 160, the outer peripheral face 1641 of dynamic vortex end plate 164 is interior with the first stop part
Stop surface (being herein presented as the inner peripheral surface 1531 determining vortex skirt section 153) keeps contact condition (for linear contact lay).That is, scroll portion is moved
Part 160 and determine radially contacting with between scroll element 150 and be a little transferred to determine vortex skirt section 153 and dynamic vortex end plate at blade
On 164.Depending on there is certain working clearance between volution blade 156 and dynamic volution blade 166.Similarly, as shown in Figure 7
Another embodiment in, dynamic vortex end plate 164 all the time with main bearing seat skirt section 143 in the state contacted.And move volution blade
166 and determine between volution blade 156 not in contact with.It follows that in the example shown in Fig. 3 and Fig. 4, at dynamic scroll element
During the translation rotation of 160, the radial outward movement of the dynamic vortex end plate 164 of dynamic scroll element 160 is entered by the first stop part
Go effective backstop, thus prevent dynamic volution blade 166 and the collision determined between volution blade 156.
It is understood that according to the radius R of the interior stop surface above for the first stop part1, dynamic vortex end plate 164
Radius ROS, and the offset E of dynamic scroll element 160 between the description of relation, at the radius R of interior stop surface1Equal to dynamic whirlpool
The radius R of the dynamic vortex end plate 164 of rotation parts 160OSWith the offset of dynamic scroll element 160 E's and (that is, ROS+E's) situation
Under, in the running that scroll compression is motor-driven, dynamic volution blade 166 with determine volution blade 156 may just contact but not to
Apply radial forces each other or contact slightly.In this case, due to first stop part footpath to dynamic scroll element
To the backstop moved out, remain able to the collision avoided or alleviate dynamic volution blade and determine between volution blade.Therefore, this
Plant to arrange and still can realize preventing or alleviating the purpose of the collision between two blades.
According to another aspect of the present utility model, stop configurations can be to be arranged in the recess 146 of main bearing seat 140
The second stop part, in order to during the translation rotation of dynamic scroll element 160, by the second stop part to dynamic scroll element
The hub portion 162 of 160 motion radially outward direction carries out backstop, alleviates or anti-fastening volution blade 156 and dynamic whirlpool
The collision of vane sheet 166.
Alternatively, as it is shown in figure 5, the second stop part can be arranged on the outer surface in the hub portion 162 of dynamic scroll element 160
On.In this case, during the translation rotation of dynamic scroll element 160, by recess 146, second stop part is stopped
Gear and then realize the backstop of the radially outer motion to the hub portion 162 of dynamic scroll element 160 such that it is able to effectively alleviate or
Person's anti-fastening volution blade 156 and the collision of dynamic volution blade 166.
In that case it is preferable that the radius R of the outer stop surface of the second stop part2Bias with dynamic scroll element 160
Amount E sum is equal to or slightly greater than the radius R of the recess 146 of main bearing seat 140R.Show with above in conjunction with shown in Fig. 3 and Fig. 4
The description of example is similar to, it is to be understood that at the radius R of the outer stop surface of the second stop part2Bias with dynamic scroll element 160
Amount E sum is equal to the radius R of the recess 146 of main bearing seat 140RIn the case of, move volution blade 166 and determine volution blade
156 may just contact but dynamic volution blade 166 is not subject to the effect of radial force or contacts the most slightly.Due to
The outer stop surface of the two stop parts backstop to the radial outward movement of dynamic scroll element, remains to be effectively prevented or alleviate two
Collision between blade.Effectively seal with to entrance further, since determine should be formed between volution blade and dynamic volution blade
Fluid in compression chamber effectively compresses, therefore, and the radius R of the outer stop surface of described second stop part2With described dynamic whirlpool
Rotation parts offset E and (that is, R2+ E) with the radius R in the female portion of described main bearing seatRBetween difference can not
Too big, and should be so that determining to form effective sealing between volution blade and dynamic volution blade.Therefore, when described second stop part
The radius R of outer stop surface2With the offset of described dynamic scroll element E's and (that is, R2+ E) slightly larger than the institute of described main bearing seat
State the radius R of recessRTime, due to second stop part backstop to the radial outward movement of dynamic scroll element, it is effectively prevented from
Dynamic volution blade and the collision phenomenon determined between volution blade, improve the service life of two blades, and improve whirlpool
The reliability of rotation compressor.
Alternatively, the second stop part can form with the hub portion 162 of dynamic scroll element 160, such as, such as Fig. 5 institute
Showing, the second stop part can be formed as the outwardly prominent annular flange flange 1621 in loose boss portion 162.With above in conjunction with Fig. 3
Similar with the embodiment that Fig. 4 describes, the second stop part can also be the single parts independent of hub portion 162.
Alternatively, the second stop part can be arranged in the approximate mid-section position of the outer surface in hub portion 162, consequently facilitating dynamic
The more stable translation rotation of scroll element 160.Alternatively, the second stop part can be along the whole outer surface in hub portion 162
Extend, i.e. in this case, the radial thickness being equivalent to hub portion is thickening.The most alternatively, the second stop part can include
Two or more second stop parts being arranged at each interval in hub portion 162.
Alternatively, in not shown example, the second stop part can also be arranged on the recess of main bearing seat 140
On the medial wall of 146.Similarly, the second stop part can also form with the medial wall of recess 146 or for independent
Parts.
In such a case, it is possible to the second stop part to be configured so that the radius of the interior stop surface of described second stop part
R3It is equal to or slightly less than the radius R in the hub portion 162 of dynamic scroll element 160H, and the offset E sum of dynamic scroll element 160
(that is, RH+E).Similarly, for making to determine to form effective sealing with to entering compression chamber between volution blade and dynamic volution blade
Interior fluid effectively compresses, the radius R of the interior stop surface of the second stop part3Radius R with hub portionHWith dynamic scroll element
Offset E and (that is, RH+ E) between difference can not be excessive.And the radius R of the interior stop surface when the second stop part3Deng
Radius R in hub portionHWith the offset of dynamic scroll element E's and time, dynamic volution blade and determine may be just between volution blade
Contact but will not collide or contact slightly.But, due to second stop part footpath to the hub portion 162 of dynamic scroll element 160
To the backstop moved out, the second stop part still is able to be effectively prevented or alleviate the collision between two blades.Such one
Come, by second stop part backstop to the radial outward movement in the hub portion 162 of dynamic scroll element 160, it is possible to effectively alleviate
Or anti-stop volution blade 166 and the collision determined between volution blade 156.
Alternatively, the second stop part can be arranged at the medium position of recess 146.Alternatively, the second stop part can
Extend with the whole medial wall along recess 146.In this case, the internal diameter being equivalent to recess 146 reduces.Also may be used
Selection of land, the second stop part can include multiple second stop parts axially arranged at each interval along recess 146.
Design above in relation to stop configurations can be designed according to the operating mode of screw compressor high speed rotating, such as may be used
To be designed under high-speed working condition ensure dynamic volution blade and determine volution blade to be exactly in the firm state contacting but will not colliding,
Thus, under relatively low speed conditions, dynamic volution blade and determine volution blade and then keep suitably being formed between seal oil
Gap.
Below in conjunction with Fig. 8-Figure 11, further illustrate according to this utility model as a example by Fig. 3 and Fig. 4 illustrated embodiment
The beneficial effect that brings of scroll compression function.Fig. 8 shows the dynamic vortex in existing scroll compressor structure as shown in Figure 2
The stress schematic diagram of parts 160 ', Fig. 9 shows the stress signal of the dynamic scroll element 160 in example as shown in Figure 3 and Figure 4
Figure.
According to Fig. 8, due to dynamic scroll element and determine to radially contact with a little at the blade of the two between scroll element,
Therefore, the total radial force (or referred to as tilting force) the dynamic volution blade of the dynamic scroll element 160 ' in existing structure being subject to
Fflank' be formulated as follows:
Fflank'=FG’+Ftg’-Fr' (formula 1)
In above-mentioned formula, FG' for moving the centrifugal force of scroll element 160 ' self, Ftg' it is that eccentric crank pin (unloads being provided with
Also include unloading lining in the case of carrying lining) it is applied to the driving force component on dynamic scroll element 160 ', Fr' it is in compression chamber
Fluid provide radial gas power.
Further, tilting moment M being applied on dynamic scroll element 160 'tilting' can be formulated as follows:
Mtilting'=(Fflank’+Fr’)*C2-FG' * C1 (formula 2)
In above-mentioned formula, C2 and C1 is respectively the arm of force of respective action power.
Similarly, according to Fig. 9, according in screw compressor of the present utility model, move scroll element and determine vortex
Contact point between parts is positioned on dynamic vortex end plate and the first stop part.Thus, dynamic scroll element 160 dynamic volution blade and
Total radial force F on dynamic vortex end plateflankAnd Fplate, and tilting moment M that is subject to of dynamic scroll element 160tiltingRespectively
It is formulated as follows:
Fflank=0 (formula 3)
Fplate=FG+Ftg-Fr(formula 4)
Mtilting=Fplate*C3+Fr*C2-FG* C1 (formula 5)
In above-mentioned formula, FGFor the centrifugal force of dynamic scroll element 160 self, Ftg(it is being provided with unloading for eccentric crank pin
Also include in the case of lining unloading lining) it is applied to the driving force component on dynamic scroll element 160, FrFor the stream in compression chamber
The radial gas power that body provides, C3 is the arm of force of respective action power.
By to the comparison between equation 1 above to formula 5 it can be clearly seen that according to whirlpool of the present utility model
In the running of rotation compressor, move volution blade and determine not contact between volution blade or just contact or connect slightly
Touch, thus the blade damage that the collision between avoiding or alleviating because of blade causes.It is additionally, since moving down of contact position,
The total tilting force F being subject on dynamic vortex end plate 164plateThe arm of force reduce, thus because of this tilting force FplateThe dynamic vortex caused
Tilting moment M of partstiltingReduce the most therewith.
With further reference to Figure 10 and Figure 11.Figure 10 and Figure 11 respectively illustrates the dynamic vortex of prior art illustrated in fig. 2
The total tilting force F being subject on parts and the dynamic volution blade according to dynamic scroll element of the present utility modelflank' and FflankWith
And heeling moment M on dynamic scroll elementtilting' and MtiltingComparison diagram.It will be clear that show at Fig. 2 from Figure 10
In the existing scroll compressor structure gone out, along with the raising of screw compressor rotating speed, the tilting force that dynamic volution blade bears
Fflank' the most increasing.And according in screw compressor of the present utility model, due to dynamic volution blade 166 with determine vortex leaf
Do not contact between sheet 156 or just contact, therefore, the tilting force F on dynamic volution blade 166flankIt is always zero.Meanwhile, root
According to Figure 11 it will be seen that the tilting moment born on dynamic scroll element in the existing scroll compressor structure shown in Fig. 2
Mtilting' increase the most rapidly along with the increase of screw compressor rotating speed.And according in screw compressor of the present utility model
Dynamic scroll element on the M that bearstiltingIt is decreased obviously, and the rotating speed of screw compressor is the highest, MtiltingRaise inconspicuous.
By analysis above, according in screw compressor of the present utility model, due to the setting of stop configurations,
Can effectively alleviate or prevent the friction damage between blade.And, moving down by contact point, efficiently reduce whirlpool
The tilting moment of rotation, reduces the risk that vortex topples.Thus, operational reliability and the performance of screw compressor are also improved.
And, screw compressor of the present utility model can make screw compressor with more on the basis of not increasing current material intensity
High rotating speed runs, and meets the demand in market.
It is understood that use according to scroll compressor structure of the present utility model, even if moving volution blade and determining whirlpool
Vane sheet there occurs collision because of other reason, due to moving down of contact point, remains to effectively reduce the tilting moment of vortex, from
And reduce the risk that vortex topples, be conducive to improving the operation stability of screw compressor.
It is understood that the screw compressor shown in Fig. 1 is high-pressure side screw compressor, i.e. by stator 122 and rotor
Air pressure environment residing for 124 drive mechanisms constituted is high pressure.But, this utility model can also be applied to low-pressure side vortex
Compressor (that is, during drive mechanism is in lower pressure environment) or other kinds of compressor.And, the first stop part herein and
Second stop part can be applied independently, it is also possible to is used in combination.Additionally, the first stop part can be fixed on housing 110, the
Two stop parts can also be arranged between the recess 146 of main bearing seat 140 and the hub portion 162 of dynamic scroll element 160, such as,
Second stop part can be fixed on the bottom of recess 146.Additionally, the exterior contour of the first stop part is not limited to circle,
For example, it is possible to be square or that other is feasible shape.
It should be noted that it is so that scroll compression function that the said structure of screw compressor of the present utility model is arranged
Premised on effectively working, therefore, to the understanding of foregoing (such as, above to " being slightly larger than ", " being slightly less than ", predetermined
The restriction of working clearance etc.) should also be as combining practical situation for the purpose of enabling to screw compressor and effectively working, and not
This purpose should be deviated from.
Although described numerous embodiments of the present utility model in detail at this, it should be appreciated that, this utility model
It is not limited to the detailed description of the invention describing in detail here and illustrating, in the feelings without departing from spirit and scope of the present utility model
Other modification and variant is may be effected by one skilled in the art under condition.It is new that all these modification and variant both fall within this practicality
In the range of type.And, all components described here can be replaced by the component of equivalent in other technologies.
Claims (14)
1. a screw compressor, it is characterised in that including:
Determine scroll element (150), described determine scroll element (150) and include determining vortex end plate (154) and be formed at and described determine vortex
End plate (154) side determine volution blade (156)；
Dynamic scroll element (160), described dynamic scroll element (160) includes dynamic vortex end plate (164), is formed at described dynamic vortex end
The dynamic volution blade (166) of plate (164) side and be formed at the hub portion (162) of described dynamic vortex end plate (164) opposite side；
Main bearing seat (140), described main bearing seat (140) supports described dynamic scroll element (160) and has for receiving described
The recess (146) of the described hub portion (162) of dynamic scroll element (160)；And
Stop configurations, described stop configurations is configured in the motor process of described dynamic scroll element (160) described dynamic vortex
Parts (160) carry out backstop described to be determined between volution blade (156) and described dynamic volution blade (166) to alleviate or to prevent
Collision.
Screw compressor the most according to claim 1, it is characterised in that described stop configurations is for being arranged in described dynamic vortex
First stop part of the periphery of end plate (164), with by the described dynamic vortex end plate (164) to described dynamic scroll element (160)
The backstop of motion in a radially outer direction alleviates or prevents from described determining volution blade (156) and described dynamic volution blade
(166) collision.
Screw compressor the most according to claim 2, it is characterised in that described first stop part has interior stop surface, institute
State the radius R of interior stop surface1Equal to or slightly less than the half of the described dynamic vortex end plate (164) of described dynamic scroll element (160)
Footpath ROSWith described dynamic scroll element (160) both offset E's and.
Screw compressor the most according to claim 3, it is characterised in that described first stop part is arranged on described determines vortex
On end plate (154).
Screw compressor the most according to claim 4, it is characterised in that described first stop part is to determine vortex end from described
Plate (154) is formed determine vortex skirt section (153) along described dynamic extending laterally of vortex end plate (164).
Screw compressor the most according to claim 3, it is characterised in that described first stop part is arranged on described base bearing
On seat (140).
Screw compressor the most according to claim 6, it is characterised in that described first stop part is from described main bearing seat
(140) the main bearing seat skirt section (143) formed along described dynamic extending laterally of vortex end plate (164).
Screw compressor the most according to claim 1, it is characterised in that described stop configurations is for being arranged on described base bearing
The second stop part in the female portion (146) of seat (140), with by the described hub portion to described dynamic scroll element (160)
(162) motion in a radially outer direction carries out backstop and alleviates or prevent from described determining volution blade (156) and described dynamic whirlpool
Collision between vane sheet (166).
Screw compressor the most according to claim 8, it is characterised in that described second stop part is arranged on described hub portion
(162) on, and the radius R of the outer stop surface of described second stop part2With the offset E's of described dynamic scroll element (160)
The radius R in the female portion (146) of the most described main bearing seat (140)R。
Screw compressor the most according to claim 9, it is characterised in that described second stop part is formed on institute
State on the outer surface of hub portion (162), or, described second stop part is fixedly connected to the described appearance of described hub portion (162)
Face.
11. screw compressors according to claim 10, it is characterised in that
Described second stop part is arranged at the medium position of described hub portion (162), or
Described second stop part extends along the whole outer surface of described hub portion (162), or
Described second stop part includes multiple second stop parts being axially spaced to arrange along described hub portion (162).
12. screw compressors according to claim 8, it is characterised in that described second stop part is arranged on described main shaft
On the medial wall in the female portion (146) of bearing (140), and the radius R of the interior stop surface of described second stop part3It is equal to
Or it is slightly less than the radius R of the described hub portion (162) of described dynamic scroll element (160)HInclined with described dynamic scroll element (160)
The sum of both heart amounts E.
13. screw compressors according to claim 12, it is characterised in that described second stop part is formed on institute
State on the described medial wall in the female portion (146) of main bearing seat (140), or described second stop part is fixedly connected to
The described medial wall in the female portion (146).
14. screw compressors according to claim 13, it is characterised in that
Described second stop part is arranged at the medium position of the female portion (146), or
Described second stop part extends along the whole inner surface of the female portion (146), or
Described second stop part includes multiple second stop parts being axially spaced to arrange along the female portion (146).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620544751.4U CN205823629U (en) | 2016-06-07 | 2016-06-07 | Scroll compressor having a plurality of scroll members |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620544751.4U CN205823629U (en) | 2016-06-07 | 2016-06-07 | Scroll compressor having a plurality of scroll members |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205823629U true CN205823629U (en) | 2016-12-21 |
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ID=57568414
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620544751.4U Withdrawn - After Issue CN205823629U (en) | 2016-06-07 | 2016-06-07 | Scroll compressor having a plurality of scroll members |
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| Country | Link |
|---|---|
| CN (1) | CN205823629U (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107476970A (en) * | 2016-06-07 | 2017-12-15 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| CN109595155A (en) * | 2017-10-03 | 2019-04-09 | 艾默生环境优化技术有限公司 | Variable volume compares compressor |
| US10753352B2 (en) | 2017-02-07 | 2020-08-25 | Emerson Climate Technologies, Inc. | Compressor discharge valve assembly |
| US10801495B2 (en) | 2016-09-08 | 2020-10-13 | Emerson Climate Technologies, Inc. | Oil flow through the bearings of a scroll compressor |
| US10890186B2 (en) | 2016-09-08 | 2021-01-12 | Emerson Climate Technologies, Inc. | Compressor |
| US10907633B2 (en) | 2012-11-15 | 2021-02-02 | Emerson Climate Technologies, Inc. | Scroll compressor having hub plate |
| US10954940B2 (en) | 2009-04-07 | 2021-03-23 | Emerson Climate Technologies, Inc. | Compressor having capacity modulation assembly |
| US10962008B2 (en) | 2017-12-15 | 2021-03-30 | Emerson Climate Technologies, Inc. | Variable volume ratio compressor |
| US10995753B2 (en) | 2018-05-17 | 2021-05-04 | Emerson Climate Technologies, Inc. | Compressor having capacity modulation assembly |
| US11655813B2 (en) | 2021-07-29 | 2023-05-23 | Emerson Climate Technologies, Inc. | Compressor modulation system with multi-way valve |
| US11846287B1 (en) | 2022-08-11 | 2023-12-19 | Copeland Lp | Scroll compressor with center hub |
-
2016
- 2016-06-07 CN CN201620544751.4U patent/CN205823629U/en not_active Withdrawn - After Issue
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11635078B2 (en) | 2009-04-07 | 2023-04-25 | Emerson Climate Technologies, Inc. | Compressor having capacity modulation assembly |
| US10954940B2 (en) | 2009-04-07 | 2021-03-23 | Emerson Climate Technologies, Inc. | Compressor having capacity modulation assembly |
| US10907633B2 (en) | 2012-11-15 | 2021-02-02 | Emerson Climate Technologies, Inc. | Scroll compressor having hub plate |
| US11434910B2 (en) | 2012-11-15 | 2022-09-06 | Emerson Climate Technologies, Inc. | Scroll compressor having hub plate |
| CN107476970A (en) * | 2016-06-07 | 2017-12-15 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| US10801495B2 (en) | 2016-09-08 | 2020-10-13 | Emerson Climate Technologies, Inc. | Oil flow through the bearings of a scroll compressor |
| US10890186B2 (en) | 2016-09-08 | 2021-01-12 | Emerson Climate Technologies, Inc. | Compressor |
| US10753352B2 (en) | 2017-02-07 | 2020-08-25 | Emerson Climate Technologies, Inc. | Compressor discharge valve assembly |
| CN109595155A (en) * | 2017-10-03 | 2019-04-09 | 艾默生环境优化技术有限公司 | Variable volume compares compressor |
| US11022119B2 (en) | 2017-10-03 | 2021-06-01 | Emerson Climate Technologies, Inc. | Variable volume ratio compressor |
| US10962008B2 (en) | 2017-12-15 | 2021-03-30 | Emerson Climate Technologies, Inc. | Variable volume ratio compressor |
| US10995753B2 (en) | 2018-05-17 | 2021-05-04 | Emerson Climate Technologies, Inc. | Compressor having capacity modulation assembly |
| US11754072B2 (en) | 2018-05-17 | 2023-09-12 | Copeland Lp | Compressor having capacity modulation assembly |
| US11655813B2 (en) | 2021-07-29 | 2023-05-23 | Emerson Climate Technologies, Inc. | Compressor modulation system with multi-way valve |
| US11879460B2 (en) | 2021-07-29 | 2024-01-23 | Copeland Lp | Compressor modulation system with multi-way valve |
| US11846287B1 (en) | 2022-08-11 | 2023-12-19 | Copeland Lp | Scroll compressor with center hub |
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