CN103912491B - Scroll compressor having a plurality of scroll members - Google Patents
Scroll compressor having a plurality of scroll members Download PDFInfo
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- CN103912491B CN103912491B CN201310006139.2A CN201310006139A CN103912491B CN 103912491 B CN103912491 B CN 103912491B CN 201310006139 A CN201310006139 A CN 201310006139A CN 103912491 B CN103912491 B CN 103912491B
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- 230000005484 gravity Effects 0.000 claims description 20
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- 230000007246 mechanism Effects 0.000 abstract description 5
- 230000006835 compression Effects 0.000 description 16
- 238000007906 compression Methods 0.000 description 16
- 239000012530 fluid Substances 0.000 description 11
- 239000008041 oiling agent Substances 0.000 description 10
- 238000000034 method Methods 0.000 description 7
- 230000008569 process Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 230000004048 modification Effects 0.000 description 4
- 238000012986 modification Methods 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 239000000314 lubricant Substances 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 239000003795 chemical substances by application Substances 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- BGOFCVIGEYGEOF-UJPOAAIJSA-N helicin Chemical compound O[C@@H]1[C@@H](O)[C@H](O)[C@@H](CO)O[C@H]1OC1=CC=CC=C1C=O BGOFCVIGEYGEOF-UJPOAAIJSA-N 0.000 description 2
- 239000003595 mist Substances 0.000 description 2
- 230000003321 amplification Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 238000002407 reforming Methods 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
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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 provide only the background information relevant to the disclosure, and it may not form prior art.
Scroll compressor generally includes determines scroll element and dynamic scroll element.The major component of determining the radial sealing force between scroll element and dynamic scroll element blade separately provides by moving the centrifugal force produced in scroll element movement process.The centrifugal force of dynamic scroll element is relevant to the rotating speed of the driving mechanism such as motor driving this dynamic scroll element.Therefore may there are the following problems: when motor rotary speed is lower, radial sealing force is too low and cause compression chamber cannot be effectively closed; And when motor rotary speed is higher, radial sealing force is too high and cause blade easily to rupture.
Therefore, a kind of scroll compressor how rational radial sealing force can both be provided regardless of motor rotary speed is needed.
Summary of the invention
According to an aspect of the present invention, provide a kind of scroll compressor, comprising: determine scroll element, described determine scroll element comprise determine vortex end plate and be formed in described determine vortex end plate side determine volution blade; Dynamic scroll element, described dynamic scroll element comprises dynamic vortex end plate, be formed in the dynamic volution blade of described dynamic vortex end plate side and be formed in the hub portion of described dynamic vortex end plate opposite side; Live axle, described live axle comprises eccentric crank pin, and described eccentric crank pin is engaged in the hub portion of described dynamic scroll element to drive described dynamic scroll element; And leverage, described leverage is constructed to be permeable to rotate with described live axle and the centrifugal force that described leverage produces due to rotation is delivered to described dynamic scroll element to offset the centrifugal force of described dynamic scroll element itself at least in part.
Accompanying drawing explanation
By the description referring to accompanying drawing, the feature and advantage of one or several mode of execution of the present invention will become easier to understand, wherein:
Fig. 1 is the longitudinal section of conventional scroll compressor;
Fig. 2 is dynamic scroll element in Fig. 1 and the schematic diagram determining the radial sealing force between scroll element;
Fig. 3 shows the partial, longitudinal cross-sectional of the scroll compressor of the leverage comprised according to first embodiment of the invention;
Fig. 4 is the assembling stereogram of the leverage according to first embodiment of the invention;
Fig. 5 is the exploded perspective view of the leverage according to first embodiment of the invention;
Fig. 6 is the side view of weight member and live axle;
Fig. 7 is according to the dynamic scroll element of first embodiment of the invention and the schematic diagram determining the radial sealing force between scroll element; And
Fig. 8 shows the partial, longitudinal cross-sectional of the leverage according to 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.Adopt identical reference character to represent identical parts in various figures, therefore the structure of same parts is by no longer repeated 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 the top cover 112 of housing 110 one end, be arranged on the bottom 114 of housing 110 the other end and be arranged between top cover 112 and housing 110 the inner space of compressor to be 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 dividing plate 116, space between housing 110 and bottom 114 form low voltage side.Low voltage side being provided with the air input joint 118 for sucking fluid, being provided with the exhaust joint 119 for the fluid after discharging compression in high pressure side.The motor 120 be made up of stator 122 and rotor 124 is provided with in housing 110.Live axle 130 is provided with to drive by the compressing mechanism determined scroll element 150 and dynamic scroll element 160 and formed in rotor 124.Dynamic scroll element 160 comprises end plate 164, be formed in the hub portion 162 of end plate side and be formed in the spiral helicine blade 166 of end plate opposite side.Determine scroll element 150 to comprise end plate 154, be formed in the spiral helicine blade 156 of end plate side and be formed in the relief opening 152 of substantial middle position of end plate.Compression chamber from radial outside to radially inner side C1, C2 and C3 of determining to be formed between the helical blade 156 of scroll element 150 and the helical blade 166 of dynamic scroll element 160 a series of volume and reducing gradually from.Wherein, the compression chamber C1 of outermost radial outside is in pressure of inspiration(Pi), and the compression chamber C3 of radial inner side is in exhaust pressure.Middle compression chamber C2 is between pressure of inspiration(Pi) and exhaust pressure, thus is also referred to as middle pressure chamber.
The side of dynamic 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 be 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 dynamic scroll element 160.By the driving of motor 120, dynamic scroll element 160 will relative to determining scroll element 150 translation rotation (namely, the central axis of dynamic scroll element 160 rotates around the central axis determining scroll element 150, but dynamic scroll element 160 itself can not rotate around the central axis of itself) to realize the compression of fluid.Above-mentioned translation rotation is realized by the cross slip-ring 190 determining to arrange between scroll element 150 and dynamic scroll element 160.Fluid after determining scroll element 150 and dynamic scroll element 160 compression is discharged to high pressure side by relief opening 152.In order to prevent on high-tension side fluid to be 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 place.
In the example of the scroll compressor shown in Fig. 1, store oiling agent in the bottom of compressor housing.Correspondingly, be formed in live axle 130 roughly along its axially extended passage, be namely formed in the center hole 136 of live axle 130 lower end and extend up to the eccentric opening 134 of eccentric crank pin 132 end face 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, feeding lubricating device can be set in this center hole 136 or in its end, such as oil pump as shown in Figure 1 or oil fork 138 etc.In the operation process of compressor, the lubricated agent feeding device supply in one end of center hole 136 has oiling agent, and the oiling agent entering center hole 136 is subject to the effect of centrifugal force and is pumped or is thrown to upwards to flow in eccentric opening 134 and along eccentric opening 134 and arrive the end face of eccentric crank pin 132 always in live axle 130 rotary course.The oiling agent of discharging from the end face of eccentric crank pin 132 along the gap between unloading lining 142 and eccentric crank pin 132 and the gap unloaded between lining 142 and hub portion 162 flow downward arrive main bearing seat 140 recess 146.The a part of oiling agent be gathered in recess 146 flows through main bearing 144 and flows downward, and a part of oiling agent is stirred by hub portion 162 and the move upward downside the thrust surfaces spread all between dynamic scroll element 160 and main bearing seat 140 along with the translation rotation of dynamic scroll element 160 that arrive the end plate 164 moving scroll element 160.In the operation process of compressor, the oiling agent be supplied on the various movable parts in compressor is thrown out of and splashes to form drop or mist.These lubricant droplet or mist will be blended in the working fluid (or refrigeration agent) that sucks from air input joint 118.These working fluids being mixed with lubricant droplet are inhaled in the compression chamber determined between scroll element 150 and dynamic scroll element 160 to realize the lubrication of these scroll element inside, sealing and cooling 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 dynamic scroll element 160.On the one hand, determine to need axial seal between the top of the helical blade 156 of scroll element 150 and the end plate 164 of dynamic scroll element 160 and between the top of the helical blade 166 of dynamic scroll element 160 and the end plate 154 determining scroll element 150.
Usually, the side contrary with helical blade 156 of the end plate 154 determining scroll element 150 is provided with back pressure cavity 158.Be provided with black box 180 in back pressure cavity 158, the axial displacement of black box 180 is subject to the restriction of dividing plate 116.Back pressure cavity 158 is pressed chamber C2 fluid to be communicated with by axially extended through hole 155 and one of them compression chamber of being formed in end plate 154 are such as middle thus form the power of will determine scroll element 150 and press towards dynamic scroll element 160.Because the side of dynamic scroll element 160 is by the upper support of main bearing seat 140, so utilize the pressure in back pressure cavity 158 effectively can will determine scroll element 150 and dynamic scroll element 160 forces together.When the pressure in each compression chamber exceedes setting value, the pressure in these compression chambers produces will exceed the downforce provided in back pressure cavity 158 with joint efforts thus make to determine scroll element 150 moves upward.Now, fluid in compression chamber by the clearance leakage between the top of the helical blade 166 of the gap between the top of helical blade 156 by determining scroll element 150 and the end plate 164 of dynamic scroll element 160 and dynamic scroll element 160 and the end plate 154 determining scroll element 150 to low voltage side to realize unloading, thus provide axial elasticity for scroll compressor.
On the other hand, also radial seal is needed between the side surface determining the side surface of the helical blade 156 of scroll element 150 and the helical blade 166 of dynamic scroll element 160.Therebetween the driving force that this radial seal provides by means of the centrifugal force of dynamic scroll element 160 in operation process and live axle 130 usually realizes.Particularly, in operation process, by the driving of motor 120, dynamic scroll element 160 will relative to determining scroll element 150 translation rotation, thus dynamic scroll element 160 will produce centrifugal force.On the other hand, the eccentric crank pin 132 of live axle 130 also can produce the driving force component contributing to realizing the radial seal determining scroll element 150 and dynamic scroll element 160 in rotary course.The helical blade 166 of dynamic scroll element 160 is determined abutting in by means of above-mentioned centrifugal force and driving force component on the helical blade 156 of scroll element 150, thus realizes radial seal therebetween.When incompressible material (such as solid impurity, lubricant oil and liquid refrigerant) enter in compression chamber be stuck between helical blade 156 and helical blade 166 time, helical blade 156 and helical blade 166 can temporarily radially be separated from each other to allow foreign matter to pass through, and therefore prevent helical blade 156 or 166 to damage.This ability that can radial separate is that scroll compressor provides radial compliance, improves the reliability of compressor.
But, along with widely using 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 the radial sealing force determined between scroll element 150 and dynamic scroll element 160.As shown in Figure 2, the total radial sealing force determined between scroll element 150 and dynamic scroll element 160 can represent with following formula:
F
flank=F
iOS+ F
ssin θ
eff-F
iO* Sin θ-F
rgformula (1)
Wherein, F
flankit is the total radial sealing force determined between scroll element 150 and dynamic scroll element 160;
F
iOSbe the centrifugal force of scroll element 160;
F
ssin θ
effthe radial component (that is, centrifugal force component) of the driving force that eccentric crank pin 132 provides, 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
iOthe centrifugal force that cross slip-ring 190 provides, θ be scroll element 160 relative to determine scroll element 150 directional angle;
F
rgthe radial gas power that the fluid in compression chamber provides.
As can be seen from above-mentioned formula 1, F
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 sealing force F
flankrelevant to the rotating speed of live axle 130.That is, the rotating speed of live axle 130 is larger, then radial sealing force F
flanklarger, and the rotating speed of live axle 130 is less, then radial sealing force F
flankless.Therefore, when scroll compressor 100 is under slow-speed of revolution operating mode, determine the radial sealing force F between scroll element 150 and dynamic scroll element 160
flankmay be not enough thus cause compressor efficiency to reduce, and when scroll compressor 100 is under high speed conditions, determine the radial sealing force F between scroll element 150 and dynamic scroll element 160
flankpossibility is excessive and cause scroll element excessive wear, even causes the broken vane of scroll element.
For the problems referred to above, make the present invention.An object of the present invention is to reduce as much as possible even eliminate live axle (or motor) rotating speed on dynamic scroll element and the impact determining the radial sealing force between scroll element.
Structure and the working principle of the scroll compressor of the leverage comprised according to first embodiment of the invention is described in detail referring to Fig. 3-8.In Fig. 3-8, have employed the numeral identical with Fig. 1 and 2 represent identical structure with letter, therefore no longer these identical structures will be carried out to the description of repetition below.
As shown in Figure 3, live axle 30 is engaged in rotor 124 to drive the translation rotation of dynamic scroll element 160.One end of live axle 30 comprises eccentric crank pin 32.Be formed in live axle 30 roughly along supplying oiling agent with the eccentric opening 34 of the first direction (longitudinal direction) of the rotation axis parallel of live axle 30 with the end to eccentric crank pin 32.The eccentric crank pin 32 of live axle 30 is engaged in the hub portion 162 of dynamic scroll element 160 via unloading lining 142.Simultaneously with reference to Fig. 4-5, eccentric crank pin 32 comprises the planar surface portion 321 of the spin axis extension being parallel to live axle 30.Correspondingly, the hole unloading the roughly D shape supplying eccentric crank pin 32 to pass of lining 142 comprises the planar surface portion 143 that can coordinate with the planar surface portion 321 of eccentric crank pin 32.Parallel with planar surface portion 143 in the radial direction, the size in hole of the roughly D shape in unloading lining 142 is greater than the size of eccentric crank pin with the radial compliance guaranteeing dynamic scroll element 160 and determine between scroll element 150.
Leverage 40 is comprised further according to scroll compressor of the present invention.Leverage 40 can be configured to rotate with live axle 30 and the centrifugal force that leverage 40 produces due to rotation can be delivered to dynamic scroll element 160, thus can offset the centrifugal force of dynamic scroll element 160 itself some or all ofly.
More specifically, the end being 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 being parallel to live axle 30.Or the plane in other words, residing for groove 323 can be parallel to the spin axis of live axle 30.Further, leverage 40 can comprise weight member 42, can being arranged in groove 323 at least partially of weight member 42, and weight member 42 can swing relative to live axle 30 around pivot points P.In addition, the center of gravity G of weight member 42 and the center of gravity of dynamic scroll element 160 can be arranged to the both sides of the spin axis being positioned at live axle 30.
Example shown in Fig. 3-6, weight member 42 is formed as roughly L shape.Long-armed 421 of L shape roughly extends along the first direction of the spin axis being parallel to live axle 30, and the galianconism 423 of L shape roughly extends along the second direction substantially vertical with first direction.Long-armed 421 of L shape can also comprise kink 422 and outwards can offset along second direction to make the center of gravity G of weight member 42.As shown in Figure 6, groove 323 can have the shape roughly corresponding with weight member 42.Weight member 42 also comprises the point of contact (or contacting part) 425 that can transmit centrifugal force to dynamic scroll element 160.More specifically, the point of contact 425 of weight member 42 transmits centrifugal force via unloading the hub portion 162 of lining 142 to dynamic scroll element 160.It should be appreciated by those skilled in the art that the shape of weight member 42 is not limited to shown in figure, on the contrary can according to the reasonable designs such as the position relationship of miscellaneous part in compressor and shape and the gravity centre distribution of revising weight member.Such as, the length of galianconism 423 can be shortened and increase its thickness.Such as, the kink 422 in long-armed 421 can be cancelled.
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 at the far-end (namely in the face of one end of dynamic vortex end plate) of eccentric crank pin 32 or its near.Structurally, pivot points P such as can be realized by the pin between weight member 42 and eccentric crank pin 32-hole cooperation.Such as, 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 by being arranged on the far-end of the eccentric crank pin 32 of live axle 30 pivotly through the pin 425 in hole 325 and 424.
The necked part 36 supported by main bearing seat 140 of live axle 30 is provided with sleeve 50 to cover a part for groove 323.And the main bearing 144 be provided with in main bearing seat 140 for supporting driving shaft 30.Sleeve 50 is between live axle 30 and main bearing 144.In addition, as shown in Figure 3, predetermined radial clearance 52 can be had between weight member 42 and sleeve 50 radially swing to allow weight member 42.
Referring to Fig. 3-7 description according to the working procedure of leverage 40 of first embodiment of the invention and the beneficial effect of generation.Because weight member 42 is fixed on live axle 30 by pin 426, so weight member 42 can rotate with live axle 30.Meanwhile, because weight member 42 can around pin 426(and pivot points P) rotate, so weight member 42 can outwards swing under the influence of centrifugal force when weight member 42 rotates with live axle 30.As shown in Figure 6, assuming that the centrifugal force produced when weight member 42 rotates is F1, point of contact 425 place is F2 to the active force that dynamic scroll element 160 transmits, distance between the center of gravity G of weight member 42 and pivot points P is H1, distance between point of contact 425 and pivot points P is H2, then according to lever principle, the pass between above-mentioned parameter is F1*1=F2*H2, i.e. F2=F1*(H1/H2).According to above-mentioned formula, the value of the F2 of expectation can be obtained by least one parameter in setpoint distance H1, H2 and F1 suitably.Particularly, in this example, because H1 is greater than H2, so leverage serves the amplification of power, therefore allow to adopt the less weight member 42 of weight to provide relatively large directed force F 2.
Become to make dynamic volution blade 166 and the radial sealing force determined between volution blade 156 and have nothing to do with the rotating speed of live axle 30, the direction of the directed force F 2 that leverage 40 can be provided is arranged to roughly contrary with the direction of the centrifugal force of dynamic scroll element 160 itself, and makes the roughly equal of the centrifugal force of the directed force F 2 of leverage 40 and dynamic scroll element 160 itself.Further, assuming that the plane residing for planar surface portion 321 of eccentric crank pin 32 and there is between the plane residing for groove 323 predetermined angle (or suppose that eccentric crank pin 32 has and effectively drive angle θ
eff), then dynamic volution blade 166 and the radial sealing force determined between volution blade 156 only can drive angle θ by above-mentioned predetermined angle or effect
effthe radial component of determined driving force provides, and has nothing to do with the centrifugal force of dynamic scroll element 160.
Effect of the present invention is explained in more detail referring to Fig. 7.As shown in Figure 7, according in the scroll compressor of first embodiment of the invention, the total radial sealing force determined between scroll element 150 and dynamic 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, the implication of other parameters and identical in formula (1).
As can be seen from above-mentioned formula 2, F
iOSalthough with the item that F2 is relevant to the rotating speed of live axle 30, pass through F
iOSto be arranged to roughly the same and direction contrary with F2, then can make difference (F therebetween
iOS-F2) be roughly zero.Particularly, no matter the rotating speed of live axle 30 how, difference (F therebetween
iOS-F2) be all roughly zero.Thus 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 equation 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, a constant can be thought.F
ssin θ
effalso be the item irrelevant with the rotating speed of live axle 30, effectively driving angle θ
effwhen fixing, a constant can be thought.
Therefore, according in the scroll compressor of first embodiment of the invention, radial sealing force F is made
flankbecome the constant irrelevant with the rotating speed of live axle 30.In other words, no matter the rotating speed of live axle 30 how, radial sealing force F
flanknot by the impact of drive shaft speed.On the other hand, due to the effective driving angle θ by changing eccentric crank pin 32
efff can be changed
ssin θ
effsize, therefore can this effectively drives angle θ by adjustment
effadjust required radial sealing force F
flank.Thus, no matter be that scroll compressor is in slow-speed of revolution operating mode or is in high speed conditions, suitable radial sealing force can be realized.Avoid the compressor efficiency caused because radial sealing force is not enough to reduce, and avoid the excessive and scroll element excessive wear that causes of radial sealing force.On the other hand, due to when designing compressor without the need to considering the change of compressor radial sealing force of scroll element under slow-speed of revolution operating mode and high speed conditions, therefore, it is possible to simplify the design of compressor thus reduce the cost of compressor.
Although in the examples described above, the equilibrant provided by leverage is set to the centrifugal force of dynamic scroll element roughly equal, but it should be appreciated by those skilled in the art that the equilibrant that leverage provides also can be set to that the centrifugal force being less than dynamic scroll element moves the centrifugal force of scroll element with partial equilibrium.In this case, the impact of compressor rotary speed change on the radial sealing force between scroll element can be reduced, thus the difference of radial sealing force under high speed conditions and slow-speed of revolution operating mode that can reduce between scroll element, this can be avoided the poor sealing of compressor under slow-speed of revolution operating mode and the excessive wear under high speed conditions.
In the structure of first embodiment of the invention, owing to have employed leverage, so the weight and volume of the weight member needed for centrifugal force of balanced dynamic scroll element can be reduced significantly, be therefore conducive to the layout of leverage within the compressor particularly in live axle.In addition, outwards offset to make the center of gravity G of weight member because weight member 42 comprises kink 422, this is equivalent to the turning radius at the center of gravity G place adding weight member 42, therefore when same weight, can provide larger centrifugal force.Sleeve 50 is set by necked part 36 place at live axle 30, groove 323 on live axle 30 can be avoided the impact of main bearing 144.In compressor of the present invention, by eccentric crank pin and the cooperation 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 just can realize above-mentioned beneficial effect without the need to carrying out change to the miscellaneous part in compressor, because this reducing the reforming cost of compressor.
Referring to Fig. 8, the leverage 40A according to second embodiment of the invention is described.In the present embodiment, leverage 40A comprises weight member 42A.Weight member 42A comprises point of contact (contacting part) 425A that can transmit centrifugal force to dynamic scroll element 160.In this example, the center of gravity G of weight member 42A is between point of contact 425A and pivot points P.That is, 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 be arranged in the groove 323 of live axle 30 pivotly via the pin-hole cooperation forming pivot points P.
More specifically, weight member 42A can comprise the first portion 421A roughly extended along the first direction of the spin axis being parallel to the live axle 30 and second portion 423A extended along the second direction substantially vertical with first direction from first portion 421A.In this example, assuming that the centrifugal force produced when weight member 42A rotates is F1 ', point of contact 425A place is F2 ' to the active force that dynamic scroll element 160 transmits, distance between the center of gravity G of weight member 42A and pivot points P is H1 ', distance between point of contact 425 and pivot points P is H2 ', then according to lever principle, the pass between above-mentioned parameter is F1 ' * H1 '=F2 ' * H2 ', i.e. F2 '=F1 ' * (H1 '/H2 ').In like manner, according to above-mentioned formula, the value of the F2 ' of expectation can be obtained by least one parameter in setpoint distance H1 ', H2 ' and F1 ' suitably.But, in this example, because H2 ' is greater than H1 ', thus leverage serve power reduce effect, therefore need to adopt weight member 42A that weight is larger to provide enough centrifugal force.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 provides to increase leverage 40A can be set further.In a kind of optimal way, the second counterweight 44 is fixed to the second portion 423A of weight member 42A by modes such as such as bolt connection, rivet interlacement.Other aspects of 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 combination and combinations.
Such as, according to an aspect of the present invention, provide a kind of scroll compressor, comprising: determine scroll element, described determine scroll element comprise determine vortex end plate and be formed in described determine vortex end plate side determine volution blade; Dynamic scroll element, described dynamic scroll element comprises dynamic vortex end plate, be formed in the dynamic volution blade of described dynamic vortex end plate side and be formed in the hub portion of described dynamic vortex end plate opposite side; Live axle, described live axle comprises eccentric crank pin, and described eccentric crank pin is engaged in the hub portion of described dynamic scroll element to drive described dynamic scroll element; And leverage, described leverage is constructed to be permeable to rotate with described live axle and the centrifugal force that described leverage produces due to rotation is delivered to described dynamic scroll element to offset the centrifugal force of described dynamic scroll element itself at least in part.
According to a second aspect of the invention, the end being 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 being parallel to described live axle.
According to a fourth aspect of the present invention, described leverage can comprise weight member, can being arranged in described groove at least partially of described weight member, and described weight member can swing relative 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 centrifugal force to described dynamic scroll element, and described point of contact can 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 being arranged on described eccentric crank pin pivotly 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 shape, and the long-armed of described L shape roughly extends along described first direction, and the galianconism of described L shape roughly extends along the second direction vertical with described first direction.
According to a ninth aspect of the present invention, the long-armed kink that comprises of described L shape makes the center of gravity of described weight member outwards offset along described second direction.
According to a tenth aspect of the present invention, described groove can have the shape roughly corresponding with described weight member.
According to an eleventh aspect of the present invention, described weight member can comprise the point of contact that can transmit centrifugal force to described dynamic scroll element, 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 is via pin-hole cooperation is arranged in the described groove of described live axle pivotly, 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 roughly extended along described first direction and the second portion extended 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 be connected with described weight member.
According to the 16 aspect of the present invention, unloading lining can be provided with between described eccentric crank pin and the hub portion of described dynamic scroll element.
According to the 17 aspect of the present invention, the point of contact of described weight member can via the hub portion transmission centrifugal force of described unloading lining to described dynamic scroll element.
According to the 18 aspect of the present invention, the necked part supported of described live axle can be arranged sleeve to cover a part for described groove by main bearing seat.
According to nineteen aspect of the present invention, between described weight member and described sleeve, predetermined radial clearance can be had.
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 that the spin axis that is parallel to described live axle extends, the plane residing for described groove and have predetermined angle between the plane residing for described planar surface portion.
According to the 22 aspect of the present invention, the numerical value of described predetermined angle can be set to and described dynamic volution blade and described radial component of determining the driving force that the radial sealing force between volution blade is all determined by described predetermined angle are provided, and has nothing to do with the centrifugal force of described dynamic 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 dynamic scroll element itself.
According to the 24 aspect of the present invention, described leverage is delivered to the active force of described dynamic scroll element can be roughly equal with the centrifugal force of described dynamic 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 dynamic 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 described in detail and illustrate here, other modification and variant can be realized when not departing from the spirit and scope of the invention by those skilled in the art.All these modification and variant all fall within the scope of the present invention.And all components described here can be replaced by component equivalent 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 in described determine vortex end plate (154) side determine volution blade (156);
Dynamic scroll element (160), described dynamic scroll element (160) comprises dynamic vortex end plate (164), be formed in the dynamic volution blade (166) of described dynamic vortex end plate (164) side and be formed in the hub portion (162) of described dynamic vortex end plate (164) opposite side;
Live axle (30), described live axle (30) comprises eccentric crank pin (32), and described eccentric crank pin (32) is engaged in the hub portion (162) of described dynamic scroll element (160) to drive described dynamic scroll element (160); And
Leverage (40,40A), described leverage (40,40A) be constructed to be permeable to described live axle (30) rotate and the centrifugal force that described leverage (40,40A) produces due to rotation is delivered to described dynamic scroll element (160) to offset the centrifugal force of described dynamic scroll element (160) itself at least in part.
2. scroll compressor as claimed in claim 1, the end being 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 being parallel to described live axle (30).
4. scroll compressor as stated in claim 3, wherein said leverage (40,40A) comprise weight member (42,42A), described weight member (42, being arranged at least partially in described groove (323) 42A), and described weight member (42,42A) can swing relative 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 centrifugal force to described dynamic scroll element (160), and described point of contact (425) is positioned between the center of gravity (G) of described weight member (42) and described pivotal point (P).
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 dynamic 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 being arranged on described eccentric crank pin (32) pivotly 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 shape, long-armed (421) of described L shape roughly extend along described first direction, and the galianconism (423) of described L shape roughly extends along the second direction vertical with described first direction.
9. scroll compressor as claimed in claim 8, long-armed (421) of wherein said L shape comprise kink (422) and the center of gravity of described weight member (42) (G) are outwards offset along described second direction.
10. scroll compressor as claimed in claim 9, wherein said groove (323) has the shape roughly corresponding with 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 centrifugal force to described dynamic scroll element (160), 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 dynamic 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) is via pin-hole cooperation is arranged in the described groove (323) of described live axle (30) pivotly, 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 the first portion (421A) that roughly extends along described first direction and the second direction substantially vertical with described first direction extend.
15. scroll compressors as claimed in claim 14, comprise the second counterweight (44) be connected with described weight member (42A) further.
16. scroll compressors according to any one of claim 5-15, are wherein provided with unloading lining (142) between described eccentric crank pin (32) and the hub portion (162) of described dynamic scroll element (160).
17. scroll compressors as claimed in claim 16, wherein said weight member (42, point of contact (425,425A) 42A) is via hub portion (162) the transmission centrifugal force of described unloading lining (142) to described dynamic scroll element (160).
18. scroll compressors according to any one of claim 4-15, the necked part (36) supported by main bearing seat (140) of wherein said live axle (30) is provided with sleeve (50) to cover a part for described groove (323).
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, in described main bearing seat (140), be wherein provided with the main bearing (144) for supporting described live axle (30), described sleeve (50) is positioned between described live axle (30) and described main bearing (144).
21. scroll compressors according to any one of claim 2-15, wherein said eccentric crank pin (32) comprises the planar surface portion (321) that the spin axis that is parallel to described live axle (30) extends, the plane residing for described groove (323) and have predetermined angle between the plane residing for described planar surface portion (321).
22. scroll compressors as claimed in claim 21, the setting value of wherein said predetermined angle becomes described dynamic volution blade (166) and described radial component of determining the driving force that the radial sealing force between volution blade (156) is all determined by described predetermined angle are provided, and has nothing to do with the centrifugal force of described dynamic scroll element (160) itself.
23. scroll compressors according to any one of 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 dynamic scroll element (160) itself.
24. scroll compressors as claimed in claim 23, the centrifugal force that wherein said leverage (40,40A) is delivered to the active force of described dynamic scroll element (160) and described dynamic scroll element (160) itself is roughly equal.
25. scroll compressors according to any one of claim 4-15, the center of gravity (G) of wherein said weight member (42,42A) and the center of gravity of described dynamic 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 CN103912491A (en) | 2014-07-09 |
| CN103912491B true CN103912491B (en) | 2016-02-24 |
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| CN111089055B (en) * | 2018-10-23 | 2024-09-06 | 谷轮环境科技（苏州）有限公司 | Scroll compressor having a rotor with a rotor shaft having a rotor shaft with a |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| JP3136820B2 (en) * | 1993-01-26 | 2001-02-19 | 株式会社日立製作所 | Scroll type fluid machine |
| CN1629486A (en) * | 2003-12-16 | 2005-06-22 | Lg电子株式会社 | Eccentric bush structure in radial compliance scroll compressor |
| CN101270751A (en) * | 2008-05-07 | 2008-09-24 | 美的集团有限公司 | Scroll compressor having a discharge port |
| CN203051113U (en) * | 2013-01-08 | 2013-07-10 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
-
2013
- 2013-01-08 CN CN201310006139.2A patent/CN103912491B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3136820B2 (en) * | 1993-01-26 | 2001-02-19 | 株式会社日立製作所 | Scroll type fluid machine |
| 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 |
| CN1629486A (en) * | 2003-12-16 | 2005-06-22 | Lg电子株式会社 | Eccentric bush structure in radial compliance scroll compressor |
| CN101270751A (en) * | 2008-05-07 | 2008-09-24 | 美的集团有限公司 | Scroll compressor having a discharge port |
| CN203051113U (en) * | 2013-01-08 | 2013-07-10 | 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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| CN103912491A (en) | 2014-07-09 |
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