CN103912491A - Scroll compressor having a plurality of scroll members - Google Patents
Scroll compressor having a plurality of scroll members Download PDFInfo
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- CN103912491A CN103912491A CN201310006139.2A CN201310006139A CN103912491A CN 103912491 A CN103912491 A CN 103912491A CN 201310006139 A CN201310006139 A CN 201310006139A CN 103912491 A CN103912491 A CN 103912491A
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- scroll
- weight member
- scroll element
- live axle
- moving
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Abstract
The invention relates to a scroll compressor (10) comprising a non-orbiting scroll member (150), an orbiting scroll member (160), a drive shaft (30) and a lever mechanism (40, 40A), the lever mechanism (40, 40A) being configured to be rotatable with the drive shaft (30) and the centrifugal force of the lever mechanism (40, 40A) due to the rotation being transmitted to the orbiting scroll member (160) to at least partially counteract the centrifugal force of the orbiting scroll member (160) itself. With the above configuration, the influence of the centrifugal force of the orbiting scroll member on the radial sealing force of the scroll member can be effectively reduced, so that a suitable radial sealing force can be achieved between the fixed scroll member and the orbiting scroll member at any rotation speed.
Description
Technical field
The present invention relates to a kind of scroll compressor.
Background technique
The content of this part only provides the background information relevant to the disclosure, and it may not form prior art.
Scroll compressor generally includes determines scroll element and moving scroll element.The major component of determining the radial seal power between scroll element and moving scroll element blade separately provides by moving the centrifugal force producing in scroll element movement process.The centrifugal force of moving scroll element is relevant to the rotating speed of for example motor of driving mechanism of this moving scroll element of driving.Therefore may there are the following problems: in the time that motor rotary speed is lower, radial seal power is too low and cause compression chamber effectively to seal; And in the time that motor rotary speed is higher, radial seal Li Taigao and cause blade easily to rupture.
Therefore, need a kind of no matter how motor rotary speed can both provide the scroll compressor of rational radial seal power.
Summary of the invention
According to an aspect of the present invention, provide a kind of scroll compressor, having comprised: determined scroll element, describedly determine scroll element and comprise and determine vortex end plate and be formed on the described volution blade of determining of determining vortex end plate one side; Moving scroll element, described moving scroll element comprises moving vortex end plate, be formed on the moving volution blade of described moving vortex end plate one side and be formed on the hub portion of described moving vortex end plate opposite side; Live axle, described live axle comprises eccentric crank pin, described eccentric crank pin is engaged in the hub portion of described moving scroll element to drive described moving scroll element; And leverage, described leverage is constructed to be permeable to be delivered to described moving scroll element to offset at least in part the centrifugal force of described moving scroll element itself with the centrifugal force that described live axle rotates and described leverage produces due to rotation.
Brief description of the drawings
By the description referring to accompanying drawing, it is easier to understand that the feature and advantage of one or several mode of execution of the present invention will become, wherein:
Fig. 1 is the longitudinal section of conventional scroll compressor;
Fig. 2 is the moving scroll element in Fig. 1 and determines the schematic diagram of the radial seal power between scroll element;
Fig. 3 shows the partial, longitudinal cross-sectional comprising according to the scroll compressor of the leverage of first embodiment of the invention;
Fig. 4 is according to the assembling stereogram of the leverage of first embodiment of the invention;
Fig. 5 is according to the exploded perspective view of the leverage of first embodiment of the invention;
Fig. 6 is the side view of weight member and live axle;
Fig. 7 is according to the moving scroll element of first embodiment of the invention and determines the schematic diagram of the radial seal power between scroll element; And
Fig. 8 shows according to the partial, longitudinal cross-sectional of the leverage of second embodiment of the invention.
Embodiment
Description related to the preferred embodiment is only exemplary below, and is never the restriction to the present invention and application or usage.In each accompanying drawing, adopt identical reference character to represent identical parts, therefore the structure of same parts will no longer be repeated in this description.
First total structure and the running principle of conventional scroll compressor are described with reference to Fig. 1.As shown in Figure 1, scroll compressor 100(hereinafter also can be called compressor sometimes) generally comprise housing 110, be arranged on housing 110 one end top cover 112, be arranged on the bottom 114 of housing 110 the other ends and be arranged on top cover 112 and housing 110 between the inner space of compressor is separated into the dividing plate 116 of high pressure side and low voltage side.Formation high pressure side, space between dividing plate 116 and top cover 112, and space between dividing plate 116, housing 110 and bottom 114 forms low voltage side.Be provided with the air input joint 118 for sucking fluid in low voltage side, be provided with the exhaust joint 119 for discharging the fluid after compression in high pressure side.In housing 110, be provided with the motor 120 being formed by stator 122 and rotor 124.In rotor 124, be provided with live axle 130 to drive the compressing mechanism forming by determining scroll element 150 and moving scroll element 160.Moving scroll element 160 comprises end plate 164, be formed on the hub portion 162 of end plate one side and be formed on the spiral helicine blade 166 of end plate opposite side.Determining scroll element 150 comprises end plate 154, is formed on the spiral helicine blade 156 of end plate one side and is formed on the relief opening 152 of the substantial middle position of end plate.Determining to form compression chamber C1, C2 and the C3 that a series of volumes are reducing to radially inner side gradually from radial outside between the helical blade 156 of scroll element 150 and the helical blade 166 of moving scroll element 160.Wherein, the compression chamber C1 of outermost radial outside is in pressure of inspiration(Pi), radially the compression chamber C3 of inner side in exhaust pressure.Middle compression chamber C2 between pressure of inspiration(Pi) and exhaust pressure, thereby be also referred to as middle pressure chamber.
One side of moving scroll element 160 is supported by the top (it forms thrust surfaces) of main bearing seat 140, and a part for live axle 130 is supported by the main bearing 144 being arranged in main bearing seat 140.One end of live axle 130 is provided with eccentric crank pin 132, is provided with unloading lining 142 between eccentric crank pin 132 and the hub portion 162 of moving scroll element 160.By the driving of motor 120, moving scroll element 160 will be with respect to determining scroll element 150 translation rotations (, move the central axis of scroll element 160 around the central axis rotation of determining scroll element 150, but moving scroll element 160 itself can not rotate around the central axis of itself) to realize the compression of fluid.Above-mentioned translation rotation realizes by the cross slip-ring 190 of determining to arrange between scroll element 150 and moving scroll element 160.Be discharged to high pressure side through the fluid of determining after scroll element 150 and 160 compressions of moving scroll element by relief opening 152.In order to prevent that on high-tension side fluid is back to low voltage side via relief opening 152 under specific circumstances, one-way valve or outlet valve 170 can be set at relief opening 152 places.
In the example of the scroll compressor shown in Fig. 1, store oiling agent in the bottom of compressor housing.Correspondingly, in live axle 130, be formed with roughly along its axially extended passage, be formed on the center hole 136 of live axle 130 lower ends and extend up to the eccentric opening 134 of eccentric crank pin 132 end faces from center hole 136.The end of center hole 136 is immersed in the oiling agent bottom compressor housing or has otherwise been supplied to oiling agent.In a kind of example, can in this center hole 136 or in its end, feeding lubricating device be set, for example oil pump as shown in Figure 1 or oil fork 138 etc.In the operation process of compressor, the lubricated agent feeding device in one end of center hole 136 is supplied with oiling agent, and the oiling agent that enters center hole 136 is subject to the effect of centrifugal force and upwards flows and arrive the end face of eccentric crank pin 132 always in being pumped or being thrown to eccentric opening 134 and along eccentric opening 134 in live axle 130 rotary courses.The oiling agent of discharging from the end face of eccentric crank pin 132 flows downward and arrives the recess 146 of main bearing seat 140 along the gap between gap and unloading lining 142 and hub portion 162 between unloading lining 142 and eccentric crank pin 132.Be gathered in a part of oiling agent in recess 146 and flow and flow downward through main bearing 144, a part of oiling agent is stirred by hub portion 162 and the downside of the end plate 164 that arrives moving scroll element 160 of moving upward spread all over the thrust surfaces between moving scroll element 160 and main bearing seat 140 along with the translation rotation of moving scroll element 160.In the operation process of compressor, be supplied to oiling agent on the comings and goings parts in compressor and be thrown out of and splash to form drop or mist.These lubricant droplet or mist will be blended in the working fluid (or refrigeration agent) sucking from air input joint 118.These working fluids that are mixed with lubricant droplet are inhaled in the compression chamber of determining between scroll element 150 and moving scroll element 160 to realize lubricated, the sealing and cooling of these scroll element inside subsequently.
In the scroll compressor shown in Fig. 1, in order to realize the compression of fluid, determining must effective sealing between scroll element 150 and moving scroll element 160.On the one hand, determine between the top of helical blade 156 of scroll element 150 and the end plate 164 of moving scroll element 160 and the top of the helical blade 166 of moving scroll element 160 and determine to need axial seal between the end plate 154 of scroll element 150.
Conventionally, be provided with back pressure cavity 158 in a side contrary with helical blade 156 of the end plate 154 of determining scroll element 150.In back pressure cavity 158, be provided with black box 180, the axial displacement of black box 180 is subject to the restriction of dividing plate 116.Thereby back pressure cavity 158 is communicated with and forms the power of pressing towards moving scroll element 160 determining scroll element 150 with for example middle pressure chamber C2 fluid of one of them compression chamber by the axially extended through hole 155 forming in end plate 154.Because a side of moving scroll element 160 is by the upper support of main bearing seat 140, so utilize pressure in back pressure cavity 158 can be effectively will to determine scroll element 150 and moving scroll element 160 forces together.In the time that the pressure in each compression chamber exceedes setting value, thereby the pressure in these compression chambers makes to determine scroll element 150 and moves upward the downforce providing in back pressure cavity 158 is provided at making a concerted effort of producing.Now, fluid in compression chamber unloads to low voltage side the top of the helical blade 166 by determine gap between the top of helical blade 156 and the end plate 164 of moving scroll element 160 of scroll element 150 and moving scroll element 160 and the clearance leakage of determining between the end plate 154 of scroll element 150 with realization, thereby provides axial elasticity for scroll compressor.
On the other hand, determine also to need radial seal between the side surface of helical blade 156 of scroll element 150 and the side surface of the helical blade 166 of moving scroll element 160.This radial seal between the two driving force that the centrifugal force in operation process and live axle 130 provide by means of moving scroll element 160 conventionally realizes.Particularly, in operation process, by the driving of motor 120, moving scroll element 160 will, with respect to determining scroll element 150 translation rotations, will produce centrifugal force thereby move scroll element 160.On the other hand, the eccentric crank pin 132 of live axle 130 also can produce the driving force component that contributes to realize the radial seal of determining scroll element 150 and moving scroll element 160 in rotary course.The helical blade 166 of moving scroll element 160 will abut on the helical blade 156 of determining scroll element 150 by means of above-mentioned centrifugal force and driving force component, thereby realizes the radial seal between the two.In the time that incompressible material (such as solid impurity, lubricant oil and liquid refrigerant) enters in compression chamber and is stuck between helical blade 156 and helical blade 166, helical blade 156 and helical blade 166 can temporarily radially be separated from each other to allow foreign matter to pass through, and have therefore prevented that helical blade 156 or 166 from damaging.This ability that can radially separate, for scroll compressor provides radial compliance, has improved the reliability of compressor.
But, along with being widely used of variable speed compressor, as above this realize the mode of radial seal by centrifugal force may there are the following problems.Fig. 2 shows the schematic diagram of determining the radial seal power between scroll element 150 and moving scroll element 160.Total radial seal power of determining between scroll element 150 and moving scroll element 160 as shown in Figure 2, can represent with following formula:
F
flank=F
iOS+ F
ssin θ
eff-F
iO* Sin θ-F
rgformula (1)
Wherein, F
flanktotal radial seal power of determining between scroll element 150 and moving scroll element 160;
F
iOSbe the centrifugal force of scroll element 160;
F
ssin θ
effthe radial component (, centrifugal force component) of the driving force that provides of eccentric crank pin 132, wherein F
sthe driving force that eccentric crank pin 132 provides, θ
effit is effective driving angle of eccentric crank pin 132;
F
iO* Sin θ is the centrifugal force component that cross slip-ring 190 provides, wherein F
iObe the centrifugal force that cross slip-ring 190 provides, θ is scroll element 160 with respect to determine scroll element 150 directional angle;
F
rgthe radial gas power that the fluid in compression chamber provides.
Can find out F from above-mentioned formula 1
iOSand F
iO* Sin θ is the item relevant to the rotating speed of live axle 130, and F
ssin θ
effand F
rgthe item irrelevant with the rotating speed of live axle 130.Therefore, radial seal power F
flankrelevant to the rotating speed of live axle 130.That is, the rotating speed of live axle 130 is larger, radial seal power F
flanklarger, and the rotating speed of live axle 130 is less, radial seal power F
flankless.Therefore,, when scroll compressor 100 is in slow-speed of revolution operating mode lower time, determine the radial seal power F between scroll element 150 and moving scroll element 160
flankthereby may not enough cause compressor efficiency to reduce, and when scroll compressor 100 is in high rotating speed operating mode lower time, determine the radial seal power F between scroll element 150 and moving scroll element 160
flankmay be excessive and cause scroll element excessive wear, even cause the blade of scroll element to break.
For the problems referred to above, make the present invention.An object of the present invention is to reduce as much as possible the rotating speed of even eliminating live axle (or motor) to moving scroll element and determining the impact of the radial seal power between scroll element.
Describe in detail and comprise according to the structure of the scroll compressor of the leverage of first embodiment of the invention and working principle below with reference to Fig. 3-8.In Fig. 3-8, adopt with numeral identical in Fig. 1 and 2 and letter and represented therefore will no longer these identical structures to be carried out the description of repetition below by identical structure.
As shown in Figure 3, live axle 30 is engaged in rotor 124 to drive moving scroll element 160 translation rotations.One end of live axle 30 comprises eccentric crank pin 32.In live axle 30, be formed with roughly eccentric opening 34 along the first direction (longitudinal direction) parallel with the spin axis of live axle 30 with the end supply of lubricant to eccentric crank pin 32.The eccentric crank pin 32 of live axle 30 is engaged in the hub portion 162 of moving scroll element 160 via unloading lining 142.With reference to Fig. 4-5, eccentric crank pin 32 comprises the planar surface portion 321 of the spin axis extension that is parallel to live axle 30 simultaneously.Correspondingly, the hole of the roughly D shape of passing for eccentric crank pin 32 of unloading lining 142 comprises the planar surface portion 143 that can coordinate with the planar surface portion of eccentric crank pin 32 321.Parallel with planar surface portion 143 in the radial direction, the size in the hole of the roughly D shape of unloading in lining 142 is greater than the size of eccentric crank pin to guarantee moving scroll element 160 and to determine the radial compliance between scroll element 150.
Further comprise leverage 40 according to scroll compressor of the present invention.The centrifugal force that leverage 40 can be configured to produce due to rotation with live axle 30 rotations and leverage 40 can be delivered to moving scroll element 160, thereby can offset the centrifugal force of moving scroll element 160 own some or all ofly.
More specifically, the end that is provided with eccentric crank pin 32 of live axle 30 can comprise groove 323.Leverage 40 can be arranged in groove 323.Groove 323 can extend along the first direction (longitudinal direction) of the spin axis that is parallel to live axle 30.Or in other words, the residing plane of groove 323 can be parallel to the spin axis of live axle 30.Further, leverage 40 can comprise weight member 42, and at least a portion of weight member 42 can be arranged in groove 323, and weight member 42 can swing with respect to live axle 30 around pivot points P.In addition, the center of gravity of the center of gravity G of weight member 42 and moving scroll element 160 can be arranged to the both sides of the spin axis that is positioned at live axle 30.
In the example shown in Fig. 3-6, weight member 42 is formed as roughly L shaped.L shaped long-armed 421 roughly extend along the first direction of the spin axis that is parallel to live axle 30, and L shaped galianconism 423 roughly extends along the second direction substantially vertical with first direction.L shaped long-armed 421 can also comprise that kink 422 can outwards be offset along second direction with the center of gravity G that makes weight member 42.As shown in Figure 6, groove 323 can have and roughly corresponding shape of weight member 42.Weight member 42 also comprises the point of contact (or contacting part) 425 that can transmit to moving scroll element 160 centrifugal force.More specifically, the point of contact 425 of weight member 42 transmits centrifugal force via unloading lining 142 to the hub portion 162 of moving scroll element 160.The shape that it should be appreciated by those skilled in the art that weight member 42 is not limited to shown in figure, on the contrary can be according to shape and the gravity centre distribution of the reasonable designs such as the position relationship of miscellaneous part in compressor and amendment weight member.For example, can shorten the length of galianconism 423 and increase its thickness.For example, can cancel the kink 422 in long-armed 421.
In this example, point of contact 425 is between the center of gravity G and pivot points P of weight member 42.Pivot points P can be positioned near the far-end (in the face of moving vortex end plate one end) of eccentric crank pin 32 or its.Structurally, pivot points P for example can coordinate to realize by the pin-hole between weight member 42 and eccentric crank pin 32.For example, weight member 42 can comprise hub switch side 42P and free end 42F.The hub switch side 42P of weight member 42 can comprise hole 424, and the far-end of eccentric crank pin 32 can comprise corresponding hole 325.Weight member 42 can be arranged on pivotly by the pin 425 through hole 325 and 424 far-end of the eccentric crank pin 32 of live axle 30.
On the necked part being supported by main bearing seat 140 36 of live axle 30, be provided with sleeve 50 to cover a part for groove 323.And in main bearing seat 140, be provided with the main bearing 144 for supporting driving shaft 30.Sleeve 50 is between live axle 30 and main bearing 144.In addition, as shown in Figure 3, between weight member 42 and sleeve 50, can there is predetermined radial clearance 52 to allow weight member 42 radially outwards to swing.
Describe according to the working procedure of leverage 40 of first embodiment of the invention and the beneficial effect of generation below with reference to Fig. 3-7.Because weight member 42 is fixed on live axle 30 by pin 426, so weight member 42 can be with live axle 30 rotations.Meanwhile, because weight member 42 can be pivot points P around pin 426() rotate, so can outwards swing under the effect of weight member 42 at centrifugal force in the time that weight member 42 rotates with live axle 30.As shown in Figure 6, suppose that the centrifugal force producing when weight member 42 rotates is F1, the active force that point of contact 425 places transmit to moving scroll element 160 is F2, distance between center of gravity G and the pivot points P of weight member 42 is H1, distance between point of contact 425 and pivot points P is H2, known according to lever principle, the pass between above-mentioned parameter is F1*1=F2*H2, i.e. F2=F1*(H1/H2).Known according to above-mentioned formula, can obtain by least one parameter in setpoint distance H1, H2 and F1 suitably the value of the F2 of expectation.Particularly, in this example, because H1 is greater than H2, so leverage has played the amplification of power, therefore allow to adopt the less weight member 42 of weight that relatively large directed force F 2 is provided.
For the radial seal power that makes moving volution blade 166 and determine between volution blade 156 becomes irrelevant with the rotating speed of live axle 30, it is roughly contrary with the direction of centrifugal force of moving scroll element 160 itself that the direction of the directed force F 2 that leverage 40 can be provided is arranged to, and the centrifugal force of the directed force F 2 that makes leverage 40 and moving scroll element 160 itself is roughly equal.Further, suppose between the residing plane of planar surface portion 321 of eccentric crank pin 32 and the residing plane of groove 323, to there is predetermined angle (or supposition eccentric crank pin 32 has effective driving angle θ
eff), moving volution blade 166 and the radial seal power of determine between volution blade 156 can be only by above-mentioned predetermined angle or effect driving angle θ
effthe radial component of determined driving force provides, and irrelevant with the centrifugal force of moving scroll element 160.
Explain in more detail effect of the present invention below with reference to Fig. 7.As shown in Figure 7, according in the scroll compressor of first embodiment of the invention, total radial seal power of determining between scroll element 150 and moving scroll element 160 can represent with following formula:
F
fiank=F
iOS+ F
ssun θ
eff-F
iO* Sin θ-F
rg-F2 formula (2)
Wherein, F2 is the centrifugal force that weight member 42 as above provides, identical with formula (1) of the implication of other parameters.
Can find out F from above-mentioned formula 2
iOSalthough be all the item relevant to the rotating speed of live axle 30 with F2, pass through F
iOSbe arranged to roughly the same and opposite direction with F2, can make the poor (F between the two
iOS-F2) be roughly zero.Particularly, no matter the rotating speed of live axle 30 is how, the poor (F between the two
iOS-F2) be all roughly zero.Thereby above-mentioned formula 2 can be reduced to following formula 3:
F
flank=F
ssin θ
eff-F
iO* Sin θ-F
rgformula (3)
In formula 3, only F
iO* Sin θ is the item relevant to the rotating speed of live axle 30.But because the weight of cross slip-ring 190 is very little, so this is almost negligible.F
rgbe the item irrelevant with the rotating speed of live axle 30, can think a constant.F
ssin θ
effalso be the item irrelevant with the rotating speed of live axle 30, effectively driving angle θ
effin fixing situation, can think a constant.
Therefore,, according in the scroll compressor of first embodiment of the invention, make radial seal power F
flankbecome the constant irrelevant with the rotating speed of live axle 30.In other words, no matter the rotating speed of live axle 30 is how, radial seal power F
flankbe not subject to the impact of drive shaft speed.On the other hand, owing to passing through to change effective driving angle θ of eccentric crank pin 32
effcan change F
ssin θ
effsize, therefore can effectively drive angle θ by adjusting this
effadjust required radial seal power F
flank.Thereby, no matter be scroll compressor in slow-speed of revolution operating mode or in high rotating speed operating mode, can realize suitable radial seal power.Avoid the compressor efficiency causing because radial seal power is not enough to reduce, and avoided the excessive and scroll element excessive wear that causes of radial seal power.On the other hand, due in design variation without considering compression machine radial seal power of scroll element under slow-speed of revolution operating mode and high rotating speed operating mode when compressor, thereby the design that therefore can simplify compressor reduces the cost of compressor.
Although in above-mentioned example, the equilibrant that leverage is provided is set for the centrifugal force that moves scroll element roughly equal, but it should be appreciated by those skilled in the art that equilibrant that leverage provides also can set the centrifugal force that is less than moving scroll element for the centrifugal force of the moving scroll element of partial equilibrium.In this case, can reduce compressor rotary speed and change the impact on the radial seal power between scroll element, thereby can reduce radial seal power between the scroll element difference under high rotating speed operating mode and slow-speed of revolution operating mode, this can be avoided the poor sealing of compressor under slow-speed of revolution operating mode and the excessive wear under high rotating speed operating mode.
In the structure of first embodiment of the invention, owing to having adopted leverage, so can reduce significantly the weight and volume of the required weight member of the centrifugal force of balanced dynamic scroll element, therefore be conducive to leverage layout in live axle particularly in compressor.In addition, be outwards offset with the center of gravity G that makes weight member because weight member 42 comprises kink 422, this has been equivalent to increase the turning radius at the center of gravity G place of weight member 42, therefore, the in the situation that of same weight, can provide larger centrifugal force.By necked part 36 places at live axle 30, sleeve 50 is set, can avoids the impact on main bearing 144 of groove 323 on live axle 30.In compressor of the present invention, by the cooperation of eccentric crank pin and unloading lining, still can keep the radial compliance of compressor.
In the present invention, leverage 40 is arranged in the groove 323 of live axle 30, therefore, substantially without the miscellaneous part in compressor is changed and just can be realized above-mentioned beneficial effect, has therefore reduced the reforming cost of compressor.
Describe according to the leverage 40A of second embodiment of the invention referring to Fig. 8.In the present embodiment, leverage 40A comprises weight member 42A.Weight member 42A comprises point of contact (contacting part) 425A that can transmit to moving scroll element 160 centrifugal force.In this example, the center of gravity G of weight member 42A is between point of contact 425A and pivot points P., pivot points P is positioned to the far-end away from eccentric crank pin 32.Similar with the first mode of execution, weight member 42A can comprise hub switch side 42AP and free end 42AF., the hub switch side 42AP of weight member 42A can coordinate and be arranged on pivotly in the groove 323 of live axle 30 via the pin-hole that forms pivot points P.
More specifically, weight member 42A can comprise roughly the 421A of first portion extending along the first direction of spin axis that is parallel to live axle 30 and the second portion 423A extending along the second direction substantially vertical with first direction from the 421A of first portion.In this example, the centrifugal force producing while supposing weight member 42A rotation is F1 ', the active force that point of contact 425A place transmits to moving scroll element 160 is F2 ', distance between center of gravity G and the pivot points P of weight member 42A is H1 ', distance between point of contact 425 and pivot points P is H2 ', known according to lever principle, the pass between above-mentioned parameter is F1 ' * H1 '=F2 ' * H2 ', i.e. F2 '=F1 ' * (H1 '/H2 ').In like manner, known according to above-mentioned formula, can obtain by least one parameter in setpoint distance H1 ', H2 ' and F1 ' suitably the value of the F2 ' of expectation.But, in this example, because H2 ' is greater than H1 ', so leverage has played the effect of dwindling of power, therefore need to adopt the weight member 42A that weight is larger that enough centrifugal force is provided.For this reason, in the leverage 40A of this example, the centrifugal force that the second counterweight 44 of being connected with weight member 42A is provided to increase leverage 40A can be further set.In a kind of optimal way, the second counterweight 44 is fixed to the second portion 423A of weight member 42A by the mode such as such as bolt connection, rivet connection.Other aspects of the second mode of execution are identical with the first mode of execution, do not repeat them here.
Specifically describe various mode of execution of the present invention and modification above, but it should be appreciated by those skilled in the art that the present invention is not limited to above-mentioned concrete mode of execution and modification but can comprises other various possible combinations and combinations.
For example, according to an aspect of the present invention, provide a kind of scroll compressor, having comprised: determined scroll element, describedly determine scroll element and comprise and determine vortex end plate and be formed on the described volution blade of determining of determining vortex end plate one side; Moving scroll element, described moving scroll element comprises moving vortex end plate, be formed on the moving volution blade of described moving vortex end plate one side and be formed on the hub portion of described moving vortex end plate opposite side; Live axle, described live axle comprises eccentric crank pin, described eccentric crank pin is engaged in the hub portion of described moving scroll element to drive described moving scroll element; And leverage, described leverage is constructed to be permeable to be delivered to described moving scroll element to offset at least in part the centrifugal force of described moving scroll element itself with the centrifugal force that described live axle rotates and described leverage produces due to rotation.
According to a second aspect of the invention, the end that is provided with described eccentric crank pin of described live axle can comprise groove, and described leverage can be arranged in described groove.
According to a third aspect of the present invention, described groove can extend along the first direction of the spin axis that is parallel to described live axle.
According to a fourth aspect of the present invention, described leverage can comprise weight member, and at least a portion of described weight member can be arranged in described groove, and described weight member can swing with respect to described live axle around pivotal point.
According to a fifth aspect of the present invention, described weight member can comprise the point of contact that can transmit to described moving scroll element centrifugal force, and described point of contact can be between the center of gravity of described weight member and described pivotal point.
According to a sixth aspect of the invention, described pivotal point can be positioned at the far-end of described eccentric crank pin.
According to a seventh aspect of the present invention, described weight member can comprise hub switch side and free end, and described hub switch side coordinates the far-end that is arranged on pivotly described eccentric crank pin via pin-hole, and described pin-hole coordinates the described pivotal point of formation.
According to an eighth aspect of the present invention, described weight member can be formed as roughly L shaped, described L shaped long-armedly roughly extend along described first direction, and described L shaped galianconism roughly extends along the second direction vertical with described first direction.
According to a ninth aspect of the present invention, describedly L shaped long-armedly comprise that kink makes the center of gravity of described weight member outwards be offset along described second direction.
According to a tenth aspect of the present invention, described groove can have and roughly corresponding shape of described weight member.
According to an eleventh aspect of the present invention, described weight member can comprise the point of contact that can transmit to described moving scroll element centrifugal force, and the center of gravity of described weight member is between described point of contact and described pivotal point.
According to a twelfth aspect of the present invention, described pivotal point can be positioned to the far-end away from described eccentric crank pin.
According to the 13 aspect of the present invention, described weight member can comprise hub switch side and free end, and described hub switch side coordinates and is arranged on pivotly in the described groove of described live axle via pin-hole, and described pin-hole coordinates the described pivotal point of formation.
According to the 14 aspect of the present invention, described weight member can comprise the first portion of roughly extending along described first direction and the second portion extending along the second direction substantially vertical with described first direction.
According to the 15 aspect of the present invention, described scroll compressor may further include the second counterweight being connected with described weight member.
According to the 16 aspect of the present invention, between the hub portion of described eccentric crank pin and described moving scroll element, can be provided with unloading lining.
According to the 17 aspect of the present invention, the point of contact of described weight member can transmit centrifugal force to the hub portion of described moving scroll element via described unloading lining.
According to the 18 aspect of the present invention, sleeve can be set to cover a part for described groove on the necked part being supported by main bearing seat of described live axle.
According to nineteen of the present invention aspect, between described weight member and described sleeve, can there is predetermined radial clearance.
According to the 20 aspect of the present invention, in described main bearing seat, be provided with the main bearing for supporting described live axle, described sleeve is between described live axle and described main bearing.
According to the 21 aspect of the present invention, described eccentric crank pin can comprise the planar surface portion of the spin axis extension that is parallel to described live axle, between the residing plane of described groove and the residing plane of described planar surface portion, has predetermined angle.
According to the 22 aspect of the present invention, the numerical value of described predetermined angle can be set for described moving volution blade and described radial seal power of determining between volution blade are all provided by the radial component of the definite driving force of described predetermined angle, and irrelevant with the centrifugal force of described moving scroll element itself.
According to the 23 aspect of the present invention, the direction of the centrifugal force that described leverage provides can be roughly contrary with the direction of the centrifugal force of described moving scroll element itself.
According to the 24 aspect of the present invention, described leverage is delivered to the active force of described moving scroll element can be roughly equal with the centrifugal force of described moving scroll element itself.
According to the 25 aspect of the present invention, the center of gravity of described weight member and the center of gravity of described moving scroll element can be positioned at the both sides of the spin axis of described live axle.
Although described various mode of execution of the present invention in detail at this, but should be appreciated that the present invention is not limited to the embodiment of describing in detail and illustrating here, in the situation that not departing from the spirit and scope of the invention, can be realized by those skilled in the art other modification and variant.All these modification and variant all fall within the scope of the present invention.And all members described here can be replaced by the member being equal in other technologies.
Claims (25)
1. a scroll compressor (10), comprising:
Determine scroll element (150), described determine scroll element (150) comprise determine vortex end plate (154) and be formed on described determine vortex end plate (154) one sides determine volution blade (156);
Moving scroll element (160), described moving scroll element (160) comprises moving vortex end plate (164), be formed on the moving volution blade (166) of described moving vortex end plate (164) one sides and be formed on the hub portion (162) of described moving vortex end plate (164) opposite side;
Live axle (30), described live axle (30) comprises eccentric crank pin (32), described eccentric crank pin (32) is engaged in the hub portion (162) of described moving scroll element (160) to drive described moving scroll element (160); And
Leverage (40,40A), described leverage (40,40A) be constructed to be permeable to be delivered to described moving scroll element (160) to offset at least in part the centrifugal force of described moving scroll element (160) itself with the centrifugal force that described live axle (30) rotates and described leverage (40,40A) produces due to rotation.
2. scroll compressor as claimed in claim 1, the end that is provided with described eccentric crank pin (32) of wherein said live axle (30) comprises groove (323), described leverage (40,40A) is arranged in described groove (323).
3. scroll compressor as claimed in claim 2, wherein said groove (323) extends along the first direction of the spin axis that is parallel to described live axle (30).
4. the scroll compressor as shown in claim 3, wherein said leverage (40,40A) comprise weight member (42,42A), described weight member (42, at least a portion 42A) is arranged in described groove (323), and described weight member (42,42A) can swing with respect to described live axle (30) around pivotal point (P).
5. scroll compressor as claimed in claim 4, wherein said weight member (42) comprises the point of contact (425) that can transmit to described moving scroll element (160) centrifugal force, and described point of contact (425) is positioned between the center of gravity (G) and described pivotal point (P) of described weight member (42).
6. scroll compressor as claimed in claim 5, wherein said pivotal point (P) is positioned at the far-end of described eccentric crank pin (32), and the distal face of described eccentric crank pin (32) is to described moving vortex end plate (164).
7. scroll compressor as claimed in claim 6, wherein said weight member (42) comprises hub switch side (42P) and free end (42F), described hub switch side (42P) coordinates the far-end that is arranged on pivotly described eccentric crank pin (32) via pin-hole, described pin-hole coordinates the described pivotal point of formation (P).
8. scroll compressor as claimed in claim 6, wherein said weight member (42) is formed as roughly L shaped, roughly extend along described first direction described L shaped long-armed (421), and described L shaped galianconism (423) roughly extends along the second direction vertical with described first direction.
9. scroll compressor as claimed in claim 8, wherein said L shaped long-armed (421) comprise that kink (422) makes the center of gravity (G) of described weight member (42) outwards be offset along described second direction.
10. scroll compressor as claimed in claim 9, wherein said groove (323) has and roughly corresponding shape of described weight member (42).
11. scroll compressors as claimed in claim 4, wherein said weight member (42A) comprises the point of contact (425A) that can transmit to described moving scroll element (160) centrifugal force, and the center of gravity (G) of described weight member (42A) is positioned between described point of contact (425A) and described pivotal point (P).
12. scroll compressors as claimed in claim 11, wherein said pivotal point (P) is positioned to the far-end away from described eccentric crank pin (32), and the distal face of wherein said eccentric crank pin (32) is to described moving vortex end plate (164).
13. scroll compressors as claimed in claim 12, wherein said weight member (42A) comprises hub switch side (42AP) and free end (42AF), described hub switch side (42AP) coordinates and is arranged on pivotly in the described groove (323) of described live axle (30) via pin-hole, and described pin-hole coordinates the described pivotal point of formation.
14. scroll compressors as claimed in claim 13, wherein said weight member (42A) comprises the second portion (423A) that roughly first portion (421A) and the second direction substantially vertical with described first direction along described first direction extension extended.
15. scroll compressors as claimed in claim 14, further comprise the second counterweight (44) being connected with described weight member (42A).
16. scroll compressors as described in any one in claim 5-15 are wherein provided with unloading lining (142) between described eccentric crank pin (32) and the hub portion (162) of described moving scroll element (160).
17. scroll compressors as claimed in claim 16, the point of contact (425,425A) of wherein said weight member (42,42A) transmits centrifugal force via described unloading lining (142) to the hub portion (162) of described moving scroll element (160).
18. scroll compressors as described in any one in claim 1-15, are provided with sleeve (50) to cover a part for described groove (323) on the necked part (36) by main bearing seat (140) supporting of wherein said live axle (32).
19. scroll compressors as claimed in claim 18, have predetermined radial clearance (52) between wherein said weight member (42,42A) and described sleeve (50).
20. scroll compressors as claimed in claim 18, wherein in described main bearing seat (140), be provided with the main bearing (144) for supporting described live axle (32), described sleeve (50) is positioned between described live axle (32) and described main bearing (144).
21. scroll compressors as described in any one in claim 2-15, wherein said eccentric crank pin (32) comprises the planar surface portion (321) of the spin axis extension that is parallel to described live axle (30), between the residing plane of described groove (323) and the residing plane of described planar surface portion (321), has predetermined angle.
22. scroll compressors as claimed in claim 21, the setting value of wherein said predetermined angle becomes described moving volution blade (166) and described radial seal power of determining between volution blade (156) are all provided by the radial component of the definite driving force of described predetermined angle, and irrelevant with the centrifugal force of described moving scroll element (160) itself.
23. scroll compressors as described in any one in claim 1-15, the direction of the centrifugal force that wherein said leverage (40,40A) provides is roughly contrary with the direction of the centrifugal force of described moving scroll element (160) itself.
24. scroll compressors as claimed in claim 23, wherein said leverage (40,40A) is delivered to the active force of described moving scroll element (160) and the centrifugal force of described moving scroll element (160) itself is roughly equal.
25. scroll compressors as described in any one in claim 4-15, the center of gravity (G) of wherein said weight member (42,42A) and the center of gravity of described moving scroll element (160) are positioned at the both sides of the spin axis of described live axle (30).
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310006139.2A CN103912491B (en) | 2013-01-08 | 2013-01-08 | Scroll compressor having a plurality of scroll members |
| US14/072,920 US9377022B2 (en) | 2013-01-08 | 2013-11-06 | Radially compliant scroll compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310006139.2A CN103912491B (en) | 2013-01-08 | 2013-01-08 | Scroll compressor having a plurality of scroll members |
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| CN103912491A true CN103912491A (en) | 2014-07-09 |
| CN103912491B CN103912491B (en) | 2016-02-24 |
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| CN201310006139.2A Active CN103912491B (en) | 2013-01-08 | 2013-01-08 | Scroll compressor having a plurality of scroll members |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111089055A (en) * | 2018-10-23 | 2020-05-01 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
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| US5520527A (en) * | 1993-12-30 | 1996-05-28 | Goldstar Co., Ltd. | Apparatus for adjusting orbital radius in a scroll compressor |
| EP0849471A4 (en) * | 1995-09-08 | 1999-08-18 | Daikin Ind Ltd | High-pressure dome type compressor in which the discharge of oil by gas is prevented and in which oil is cooled by discharge gas |
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| CN111089055A (en) * | 2018-10-23 | 2020-05-01 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
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| CN103912491B (en) | 2016-02-24 |
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