CN103807166A - Scroll compressor having a plurality of scroll members - Google Patents
Scroll compressor having a plurality of scroll members Download PDFInfo
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- CN103807166A CN103807166A CN201210456871.5A CN201210456871A CN103807166A CN 103807166 A CN103807166 A CN 103807166A CN 201210456871 A CN201210456871 A CN 201210456871A CN 103807166 A CN103807166 A CN 103807166A
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Abstract
The present invention relates to a scroll compressor, comprising: a non-orbiting scroll member (50) including a non-orbiting scroll end plate (54) and non-orbiting scroll blades (56); an orbiting scroll member (60, 60A, 60B, 60C, 60E) including an orbiting scroll end plate (64), an orbiting scroll vane (66), a hub (62), and a thrust surface (68); a main bearing housing (40, 40D, 40E) including a support portion (42) that axially supports a thrust surface of the orbiting scroll member and a recess (46) that receives a hub portion (62) of the orbiting scroll member to enable translational rotation of the hub portion therein; and a lubricant supply passage (OP) configured to supply lubricant from the recess (46) to one of the compression chambers (C1) or a vicinity thereof. By adopting the invention, the lubricant can be better supplied to the compression cavity.
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 the compressing mechanism forming by determining scroll element and moving scroll element.Conventionally, determine scroll element and moving scroll element is realized lubricated by so-called mist of oil.Particularly, the oiling agent in compressor is because the motion of comings and goings parts in compressor forms drop or mist and is blended in working fluid.Be blended in these lubricant droplet in working fluid or mist and from the intakeport of compressing mechanism, suck lubricated to play in a series of compression chambers of determining to limit between scroll element and moving scroll element, sealing, the effect such as cooling.
But, in some cases, can not make compressing mechanism obtain sufficient lubrication by the mode of this oil mist lubrication.Therefore, hope can realize the lubricated of compressing mechanism in better mode.
Summary of the invention
According to embodiment of the present invention aspect, provide a kind of scroll compressor.This scroll compressor can comprise: determine scroll element, describedly determine scroll element and comprise and determine vortex end plate and be formed on describedly to determine spiral helicine on vortex end plate and determine volution blade, moving scroll element, described moving scroll element comprises moving vortex end plate, be formed on the spiral helicine moving volution blade of described moving vortex end plate the first side, be formed on the hub portion of described moving vortex end plate the second side and be formed in described second side of described moving vortex end plate and be positioned at the thrust surfaces of the radial outside of described hub portion, described moving volution blade and describedly determine volution blade and be engaged with each other to form betwixt a series of compression chambers, the volume of described compression chamber reduces towards its radially inner side from the described radial outside of determining scroll element in respect to described process of determining scroll element translation rotation gradually at described moving scroll element, main bearing seat, the described hub portion that described main bearing seat comprises the supporting portion of the thrust surfaces of moving scroll element described in axially support and receives described moving scroll element is to make the recess of described hub portion translation rotation therein, and oiling agent supply passage, near described oiling agent supply passage is configured to that oiling agent is supplied to one of them compression chamber or its from described recess.
Accompanying drawing explanation
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 according near the longitudinal section moving scroll element of first embodiment of the invention and main bearing seat;
Fig. 3 A and 3B are respectively according to the top and bottom perspective views of the moving scroll element of first embodiment of the invention;
Fig. 4 is according to the moving scroll element of first embodiment of the invention and determines the schematic diagram of the variation of the compression chamber between scroll element;
Fig. 5 is the plan view of main bearing seat;
Fig. 6 is according near the longitudinal section moving scroll element of second embodiment of the invention and main bearing seat;
Fig. 7 A and 7B are respectively according to the top and bottom perspective views of the moving scroll element of second embodiment of the invention;
Fig. 8 is according near the longitudinal section moving scroll element of third embodiment of the invention and main bearing seat;
Fig. 9 is according near the longitudinal section moving scroll element of four embodiment of the invention and main bearing seat;
Figure 10 is according near the longitudinal section moving scroll element of fifth embodiment of the invention and main bearing seat;
Figure 11 is according to the plan view of the main bearing seat of fifth embodiment of the invention; And
Figure 12 A and 12B are according near the longitudinal section moving scroll element of sixth embodiment of the invention and main bearing seat, show respectively different working staties.
Embodiment
Be only exemplary to the description of the various mode of executions of the present invention below, and be 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 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 vortex 150 and the helical blade 166 of moving vortex 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 (being supporting portion) of main bearing seat 140, and one end of 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 (, the central axis of moving scroll element 160 is around the central axis rotation of determining scroll element 150, but moving scroll element 160 itself can not rotate around the central axis of self) 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 order to realize the compression of fluid, determining needs 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 middle pressure chamber C2 fluid and is formed the power of pressing towards moving vortex 160 determining scroll element 150 by the axially extended through hole (not shown) forming in end plate 154.Because a side of moving vortex 160 is supported by the supporting portion 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 and contribute to realize the driving force component of determining scroll element and moving scroll element radial seal 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.
To the greasing of each parts in compressor be described below.In the example of the vertical vortex 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, feeding lubricating device can or be set, for example oil pump as shown in Figure 1 or oil fork 138 etc. in this center hole 136 near it.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 order to improve the lubrication and cooling effect of rotor 124 of motor, can in live axle 130, arrange radial hole 139 with from eccentric opening 134 directly to rotor 124 supply of lubricant.In addition, radial hole 137 can also be set in live axle 130 with the direct direct supply of lubricant of lower bearing to supporting driving shaft 130 lower ends.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.Moving scroll element and this lubricating of determining between scroll element are referred to as oil mist lubrication conventionally.
But, under some specific operation, this oil mist lubrication cannot and be determined scroll element to moving scroll element and supply with enough oiling agents, and this can increase moving scroll element and determines the wearing and tearing of scroll element and can affect the sealing effect between the two, thereby causes the hydraulic performance decline of whole compressor.For example, in the time adopting the inverter motor of variable speed, in the time that the rotating speed of motor is higher, the amounts of lubrication that is supplied to moving scroll element and determine in scroll element may be proper, but in the time that the rotating speed of motor is lower, is supplied to moving scroll element and determine the obviously deficiency of amounts of lubrication in scroll element.Therefore, expect the oiling agent of compressing mechanism to supply with and improve.
Describe according to the structure of the scroll compressor of various mode of executions of the present invention below with reference to Fig. 2 to Figure 12 B.It is worthy of note, various mode of executions below relate generally to the moving scroll element in scroll compressor and/or the improvement of main bearing seat, and therefore the structure of the miscellaneous part in scroll compressor and working principle will repeat no more.
Fig. 2 shows according near the longitudinal section moving scroll element 60 in the scroll compressor of first embodiment of the invention and main bearing seat 40.Fig. 3 A and 3B show respectively the top and bottom perspective views of moving scroll element 60.
As shown in Figure 2, can comprise and determine scroll element 50 and moving scroll element 60 according to the scroll compressor of first embodiment of the invention.Determining scroll element 50 comprises and determines vortex end plate 54 and be formed on to determine spiral helicine on vortex end plate 54 and determine volution blade 56.Moving scroll element 60 comprises moving vortex end plate 64, is formed on the spiral helicine moving volution blade 66 of moving vortex end plate 64 first sides, is formed on the hub portion 62 of moving vortex end plate 64 second sides and is formed on the thrust surfaces 68 of moving in vortex end plate 64 second sides and being positioned at the radial outside of hub portion 62.Move volution blade 66 and determine volution blade 56 and be engaged with each other to form betwixt a series of compression chamber C1, C2 and C3.The volume of these compression chambers reduces towards its radially inner side from the radial outside of determining scroll element 50 or moving scroll element 60 in the process of scroll element 50 translation rotations with respect to determining gradually at moving scroll element 60, to realize the compression of fluid.
Fig. 4 shows the moving volution blade 66 of moving scroll element 60 and determines the change procedure of determining the compression chamber between volution blade 56 of scroll element 50.In the position shown in (a) of Fig. 4, outermost compression chamber C1 is in breathing process, and middle compression chamber C2 is in compression process, and inboard compression chamber C3 is also in compression process.In the position shown in (b) of Fig. 4, along with the translation rotation of moving scroll element 60, outermost compression chamber C1 continues air-breathing and is about to closedly, and inboard compression chamber C3 is by exhaust.In the position shown in (c) of Fig. 4, along with the translation rotation of moving scroll element 60, outermost compression chamber C1 completes air-breathing and reaches its maximum volume, now because moving volution blade 66 is completely closed with determining volution blade 56 to engage at outermost radial outside place.In this position, inboard compression chamber C3 carries out exhaust in addition.Thus, from position (a) to position (b) to position, (c) completes first compression circulation.In upper once compression cycle, due to moving volution blade with determine the moving inward along helix at the bonding point of volution blade, the position that is positioned at outermost compression chamber in last compression cycle moves inward gradually and its volume diminishes gradually, thus, in last compression cycle, be positioned at outermost compression chamber and become middle compression chamber, and form the new outermost compression chamber that is positioned at simultaneously.
Get back to Fig. 2, also comprise main bearing seat 40 according to the scroll compressor of first embodiment of the invention.Main bearing seat 40 can comprise that the supporting portion 42 of thrust surfaces 68 of the moving scroll element 60 of axially support and the hub portion 62 that receives moving scroll element 60 are to make the recess 46 of hub portion 62 translation rotation therein.
As described with reference to FIG. 1, in the first mode of execution shown in Fig. 2, scroll compressor further comprises the live axle 130 that drives moving scroll element 60.Live axle 130 can be supported by main bearing seat 40.More specifically, live axle 130 can be supported by main bearing seat 40 in rotating mode via the main bearing 144 being for example arranged in main bearing seat 40.The eccentric crank pin 142 of live axle 130 can be engaged in the hub portion 62 of moving scroll element 60 and move scroll element 60 translation rotations with driving via unloading lining 142.Live axle 130 can comprise along the passage 135 that roughly axial direction extends.More specifically, this passage 135 can comprise as shown in Figure 1 with the concentric center hole 136 of live axle 130 with respect to the eccentric opening 134 of center hole 136 bias.The first end of this passage 135 is communicated with recess 46 fluids of main bearing seat 40, and the second end of this passage 135 can be supplied to oiling agent.For example, can as shown in Figure 1, second end (lower end) of live axle 130 be immersed in the oiling agent memory section of compressor housing bottom, can also feeding lubricating device be set at the second end of this passage 135, such as oil pump 138 etc.
Further comprise from the recess 46 of main bearing seat 40 to determining wherein one or more compression chambers between scroll element 50 and moving scroll element 60 or near the oiling agent supply passage OP of supplying lubricating oil it according to the scroll compressor of first embodiment of the invention.In other words, near this oiling agent supply passage OP can be configured to extend to one of them compression chamber or its from the recess 46 of main bearing seat 40.In the example shown in Fig. 2, oiling agent supply passage OP can be formed in the moving vortex end plate 64 of moving scroll element 60 and can comprise lubricant entry 11 and lubricant outlet 12, and near oiling agent supply passage OP extends to outermost compression chamber C1 or its from recess 46.In other words, oiling agent supply passage OP extends near of the outermost part of moving volution blade 66 from recess 46, or extends to by moving scroll element and determine near the intakeport of the compressing mechanism that scroll element forms.Lubricant entry 11 is formed on the radial outside of the hub portion 62 of moving scroll element 60.It should be appreciated by those skilled in the art that the different designs that depends on scroll element, oiling agent supply passage OP also may from recess 46 extend to other compression chamber C1 or its near.
In the example shown in Fig. 2,3A and 3B, lubricant entry 11 can be formed on second side (being formed with that side of thrust surfaces 68) of moving vortex end plate 64, and lubricant outlet 12 can be formed on first side (being formed with that side of moving volution blade 66) of moving vortex end plate 64.In moving vortex end plate 64, can be formed with the communicating passage 13 that lubricant entry 11 and lubricant outlet 12 fluids are communicated with.For example, the radially extension along moving scroll element 60 that communicating passage 13 can approximate horizontal.
Oiling agent supply passage OP can form by for example following process: the second sidetracking of driven vortex end plate 64 goes out lubricant entry 11, the first sidetracking of driven vortex end plate 64 goes out lubricant outlet 12, the side of driven vortex end plate 64 gets out communicating passage 13, and the outermost opening of communicating passage 13 is sealed with plug 14.Therefore, can on original moving scroll element 60, form this oiling agent supply passage OP by simple machining, therefore not need to change the injection molding die of moving scroll element 60, thus the manufacture cost of having saved whole scroll compressor.It should be appreciated by those skilled in the art that and can also adopt other modes to form this oiling agent supply passage OP, for example, in injection molded process, form this oiling agent supply passage OP.
According in the scroll compressor of first embodiment of the invention, can also comprise be configured to by oiling agent from recess 46 be supplied to a series of compression chambers another or its near the second oiling agent supply passage OP '.The second oiling agent supply passage OP ' can have the similar structure with oiling agent supply passage OP, does not therefore repeat them here.The second oiling agent supply passage OP ' can be formed as the central axis symmetry about moving scroll element with oiling agent supply passage OP, but the present invention is not limited thereto.In this way, can, simultaneously to outermost compression chamber C1 and the C1 supply of lubricant of two substantial symmetry, make more all even abundances of supply of oiling agent.
The supply process of oiling agent is described below with reference to Fig. 2.The oiling agent of discharging from the passage 135 of live axle 130 as shown in Figure 2, will be gathered in the recess 46 of main bearing seat 40.Along with the translation rotation in recess 46 of the hub portion 62 of moving scroll element 60, the oiling agent in recess 46 is subject to the effect of centrifugal force and forms as the roughly parabolic liquid level of being indicated by OL in Fig. 2.Under the direct draught that oiling agent in this liquid level OL produces at centrifugal force and the air-breathing negative pressure causing at compressing mechanism, be inhaled into from lubricant entry 11, then be discharged to outermost compression chamber C1, as shown in the arrow in Fig. 2 from lubricant outlet 12 through communicating passage 13.Can be simultaneously with reference to figure 4, (a) in Fig. 4 and position (b), thus lubricant outlet 12 all contributes to aspirate oiling agent from recess 46 in pressure of inspiration(Pi) and because the translation rotation of moving scroll element can produce certain negative pressure at lubricant outlet 12 places.
In the first mode of execution of the present invention shown in Fig. 2, the compression chamber of determining between scroll element 50 and moving scroll element 60 passes through two kinds of mode supply of lubricant, i.e. oil mist lubrication mode of the prior art and the mode according to oiling agent supply passage OP of the present invention.Therefore, in compression chamber, enough oiling agents be can be supplied to, the excessive wear that causes due to lubricant starvation or the problem of hydraulic performance decline avoided.
But, be not that the amounts of lubrication of supplying with to compression chamber is the bigger the better, too high amounts of lubrication also can cause the decline of compressor performance.In the first mode of execution of the present invention, for example, can adjust or determine the target oiling agent delivery volume of supplying with to moving scroll element 60 by the shape of suitable design oiling agent supply passage OP or cross-section area.For example, the cross-section area of oiling agent supply passage OP is larger, and target oiling agent delivery volume is larger.For example, the shape of oiling agent supply passage OP more level and smooth (being that flow resistance is less), target oiling agent delivery volume is larger.In this case, oiling agent supply passage OP can be configured so that recess 46 and one of them compression chamber communicate with each other continuously with continuous supply of lubricant.
In the first mode of execution of the present invention, can also regulate or control the target oiling agent delivery volume of supplying with to moving scroll element 60 by designing suitably the position of lubricant entry 11.
Specifically describe below with reference to the various parameters that provide in Fig. 5 the method for controlling target oiling agent delivery volume by the position of lubricant entry 11.Fig. 5 is the plan view of main bearing seat 40, in Fig. 5, the internal diameter of supposing recess 46 is R, and the turning radius of the translation rotation of moving scroll element 60 is the circle that r(forms referring to two dot and dash line in Fig. 5), the distance between lubricant entry 11 and the central axis O of recess 46 is a., in the time of a<R-r, lubricant entry 11 is always communicated with recess 46 fluids.In addition, in the time of a>R+r, lubricant entry 11 is covered by the supporting portion 42 of main bearing seat 40, so lubricant entry 11 is not always communicated with recess 46 fluids.
In first embodiment of the invention, in order to control suitably target oiling agent delivery volume, the radial position of lubricant entry 11 on moving vortex end plate 64 can be designed so that above-mentioned parameter meets formula: R-r<a<R+r.In this case, oiling agent supply passage OP can be configured so that recess 46 and compression chamber intermittently communicate with each other.Particularly, lubricant entry 11 has the translation rotation along with moving scroll element 60 in the scope of dot and dash line circle (circle on right side) of radius r and moves in Fig. 5, in the time that the supported portion 42 of lubricant entry 11 covers, stop supply of lubricant, and in the time that the not supported portion 42 of lubricant entry 11 covers, start supply of lubricant.Therefore the ratio between the time that the time that, can cover by the control supported portion 42 of lubricant entry 11 and not supported portion 42 cover is controlled target oiling agent delivery volume.
More specifically, suppose that determining the line between lubricant entry 11 and the central axis O of recess 46 in scroll element 60 translation rotation processes and be θ through the angle between the radial line OA of the central axis O of recess 46, the maximum value of angle is θ
max, the percentage of time that lubricant entry 11 is communicated with recess 46 is η.Above-mentioned parameter meets following formula:
According to above-mentioned formula, the target oiling agent delivery volume of supplying with to moving scroll element 60 can determine according to η, and wherein η is larger, and target delivery volume is larger.Or in other words, in the time having determined target oiling agent delivery volume (being η), can from above-mentioned formula, derive the occurrence of parameter a, and can further determine the radial position (, distance lubricant entry 11 and the central axis of moving scroll element 60 between) of lubricant entry 11 on moving vortex end plate 64.
As mentioned above, in first embodiment of the invention, can carry out the target oiling agent delivery volume of suitable control to moving scroll element by the position of shape, cross-section area and the lubricant entry of control oiling agent supply passage OP.Therefore, can control suitably the ride quality of target oiling agent delivery volume with optimum compression machine.
Describe second embodiment of the invention below with reference to Fig. 6,7A and 7B.Fig. 6 shows according near the longitudinal section moving scroll element 60A of second embodiment of the invention and main bearing seat 40; Fig. 7 A and 7B show respectively according to the top and bottom perspective views of the moving scroll element 60A of second embodiment of the invention.
Difference between the second mode of execution and the first mode of execution is, the communicating passage of oiling agent supply passage OP is formed as the groove 13A extending in the second side of moving vortex end plate 64.In this case, lubricant entry 11 is made up of the radial inner end of groove 13A, and lubricant outlet 12 is formed as extending through moving vortex end plate 64 and arrives the radial outer end of groove 13A.Other aspects and first mode of execution of the second mode of execution are similar, therefore repeat no more.
Be similar to the first mode of execution, in the second mode of execution, also can form the second oiling agent supply passage OP ' with more equal even supply of lubricant fully.
With reference to Fig. 6, in the second mode of execution, the oiling agent in recess 46 can be supplied in compression chamber via lubricant entry 11, groove 13A and lubricant outlet 12.In the example shown in Fig. 6, in the process of moving scroll element 60 translation rotations, the supported portion 42 of a part of groove 13A seals to form the passage of sealing, and a part of groove 13A is outstanding to be exceeded supporting portion 42 and open wide.Even in this case, due to the negative pressure forming in compression chamber, still can successfully oiling agent be drawn in compression chamber via lubricant outlet 12.
The second mode of execution of the present invention, except can realizing the beneficial effect of the first mode of execution, can also be achieved as follows beneficial effect.In the second mode of execution, replace the communicating passage 13 in the first mode of execution with groove 13A, thus the plug 14 for sealing communicating passage 13 omitted, thus further provide cost savings and simplified manufacturing process.For example,, because oiling agent has passed through the stayed surface (being thrust surfaces) of supporting portion 42, so can supply with more sufficient oiling agent to guarantee better the steady running of compressor to the thrust surfaces between moving scroll element and main bearing seat.
Describe according to the 3rd mode of execution of the present invention below with reference to Fig. 8.Fig. 8 shows according near the longitudinal section moving scroll element 60B of third embodiment of the invention and main bearing seat 40.
Difference between the 3rd mode of execution and the first mode of execution is, oiling agent supply passage OP communicating passage 13B is configured to extend obliquely.Other aspects and first mode of execution of the 3rd mode of execution are similar, therefore repeat no more.
In the 3rd mode of execution, can only adopt a drilling operation form oiling agent supply passage OP and can omit plug.Therefore,, except the beneficial effect of above-mentioned mode of execution, the 3rd mode of execution can further be simplified the manufacturing process of oiling agent supply passage OP and therefore reduce the manufacture cost of compressor.
Describe according to the 4th mode of execution of the present invention below with reference to Fig. 9.Fig. 9 shows according near the longitudinal section moving scroll element 60C of four embodiment of the invention and main bearing seat 40.
Difference between the 4th mode of execution and the first mode of execution is, oiling agent supply passage OP also comprises the second lubricant outlet 12C, the second lubricant outlet 12C be formed on the first side of moving vortex end plate 64 and be arranged in compression chamber another or its near.In other words, in the 4th mode of execution, the second side at moving vortex end plate 64 is formed with a lubricant entry 11, the first side at moving vortex end plate 64 is formed with two lubricant outlets 12 and 12C, and two lubricant outlets 12 and 12C are by a communicating passage 13C and lubricant entry 11 fluid passages.Two lubricant outlets 12 and 12C can extend to respectively near different compression chambers or its, preferably, can extend near two outermost compression chambers in symmetrical position roughly or its.Other aspects and first mode of execution of the 4th mode of execution are similar, therefore repeat no more.
In the 4th mode of execution, can form two oiling agent supply passage OP described in the first mode of execution and OP ' and can omit a plug with drilling operation still less.Therefore,, except the beneficial effect of above-mentioned mode of execution, the 4th mode of execution can further be simplified the manufacturing process of oiling agent supply passage and better lubrication effect is provided.
Describe according to the 5th mode of execution of the present invention below with reference to Figure 10 and 11.Figure 10 shows according near the longitudinal section moving scroll element 60 of fifth embodiment of the invention and main bearing seat 40D; Figure 11 shows according to the plan view of the main bearing seat 40D of fifth embodiment of the invention.
In the 5th mode of execution, identical with the first mode of execution of the structure of moving scroll element 60, therefore repeats no more.But the structure of the main bearing seat 40D of the 5th mode of execution is different from the first mode of execution.Particularly, in the 5th mode of execution, the supporting portion 42 of main bearing seat 40D comprises the stayed surface 44 contacting with the thrust surfaces 68 of moving scroll element 60, is formed with annular groove 47 in stayed surface 44.In the example shown in Figure 11, annular groove 47 is communicated with recess 46 fluids via the roughly groove 48 being radially arranged on stayed surface 44.Annular groove 47 can be configured in the translation rotation process of moving scroll element 60 can with lubricant entry 11 intermittently fluid be communicated with.Particularly, in the position shown in Figure 10, the lubricant entry 11 of oiling agent supply passage OP is communicated with recess 46 fluids, and the lubricant entry 11 ' of oiling agent supply passage OP ' is communicated with annular groove 47 fluids.
The 5th mode of execution can also be achieved as follows beneficial effect except can realizing the beneficial effect of above-mentioned mode of execution.For example, owing to being provided with annular groove 47, likely simultaneously to two oiling agent supply passage supply of lubricant, and meanwhile can also provide more lubricated for the thrust surfaces between moving scroll element and main bearing seat.
It should be appreciated by those skilled in the art that the corresponding beneficial effect that can be combined with to realize with moving scroll element 60,60A, 60B and the 60C of above-mentioned first to fourth mode of execution according to the main bearing seat 40D of the 5th mode of execution.
Describe according to the 6th mode of execution of the present invention below with reference to Figure 12 A and 12B.Figure 12 A and 12B show respectively according near the longitudinal section moving scroll element 60E of sixth embodiment of the invention and main bearing seat 40E.
In the 6th mode of execution, as shown in Figure 12 A and 12B, the supporting portion 42 of main bearing seat 40E comprises the stayed surface 44 contacting with the thrust surfaces 68 of moving scroll element 60, is formed with annular groove 47 in stayed surface 44.Annular groove 47 is communicated with recess 46 fluids via the lubricant passageway OPA being arranged in the main body portion (being recess 46 sidewall around) of main bearing seat 40.Similar in the structure of moving scroll element 60E and the first mode of execution, but the lubricant entry 11 that is formed in the oiling agent supply passage OP in moving scroll element 60E is configured to the scope that is positioned at all the time the stayed surface 44 of the supporting portion 42 of main bearing seat 40E in scroll element 60 translation rotation processes moving.Thus, annular groove 47 can be in the translation rotation process of moving scroll element 60 with lubricant entry 11 intermittently fluid be communicated with.
Utilize above-mentioned structure, the lubricant oil in recess 46 can be supplied in wherein one or more compression chambers or near it via the oiling agent supply passage OP in the lubricant passageway OPA in main bearing seat 40E and moving scroll element 60E.
In order to control better or to regulate target oiling agent delivery volume, control gear 70 can be set in lubricant passageway OPA.Control gear 70 is constructed to be permeable to optionally open or close lubricant passageway OPA.Particularly, lubricant passageway OPA can comprise the duct 49-1 and the edge duct 49-2 that roughly axial direction forms that form along general radial direction.Duct 49-1 and 49-2 communicate with each other.Duct 49-1 extends to the outside of main bearing seat 40E from recess 46.Can control gear 70 be installed from the outer openings of duct 49-1 utilizes control gear 70 to seal the outer openings of duct 49-1 simultaneously.
In the example shown in Figure 12 A and 12B, control gear 70 is configured to pressure controlled valve 70.When the pressure that pressure controlled valve 70 is configured to be subject at it is less than or equal to predetermined value, open lubricant passageway OPA(and see Figure 12 A) and the pressure being subject at it close lubricant passageway OPA(while being greater than predetermined value and see Figure 12 B).More specifically, pressure controlled valve 70 can comprise piston 72 and provide the spring 74 of bias force for piston.In piston 72, include fluid passage 73.In the time that the pressure in lubricant passageway OPA (acting on the pressure on piston 72) is less than or equal to predetermined value, thereby align and allow lubricant passageway OPA to be communicated with duct 49-2 in the fluid passage 73 in piston 72.In the time that the pressure in lubricant passageway OPA is greater than predetermined value, piston 72 is promoted to make fluid passage 73 and duct 49-2 to stagger to radial outside, thereby other parts of piston 72 have been blocked lubricant passageway OPA.
From the running principle of scroll compressor, in the time driving the rotating speed of the motor 120 that rotates of live axle 130 higher, in recess 46, due to centrifugal force, to be formed as hydraulic pressure in parabolic oiling agent liquid level higher.Therefore, when the rotating speed of motor 120 is compared with high and need to reduce target oiling agent delivery volume time, control gear 70 cuts out lubricant passageway OPA because the hydraulic pressure in lubricant passageway OPA is greater than predetermined value, thereby stops to compression chamber supply of lubricant.And when the rotating speed of motor 120 is compared with low and need to increase target oiling agent delivery volume time, thereby the fluid passage 73 that control gear 70 is promoted in piston 72 to radially inner side by spring 74 because the hydraulic pressure in lubricant passageway OPA is less than predetermined value has been communicated with duct 49-1 and 49-2.Therefore control gear 70 has been opened lubricant passageway OPA and has been started to compression chamber supply of lubricant.
It is worthy of note, in above-mentioned structure, control gear 70 opens and closes the pilot pressure (being above-mentioned predetermined value) of lubricant passageway OPA and can control by spring 74, for example, can set suitable pilot pressure (being above-mentioned predetermined value) for spring arranges suitable spring constant in advance.
In another kind of example, control gear 70 can be configured to electronic control valve.Described electronic control valve can be configured to open lubricant passageway OPA and close lubricant passageway OPA during in power-off in when energising, or described electronic control valve is opened lubricant passageway OPA can be configured at closed in electrified state lubricant passageway OPA and in power-off time.In addition, electronic control valve can be controlled according to the operating condition of scroll compressor.For example, electronic control valve can be configured to according to the rotating speed of motor that drives moving scroll element 60 control make in the time that the rotating speed of motor is more than or equal to predetermined value electronic control valve close lubricant passageway OPA and in the time that the rotating speed of motor is less than predetermined value electronic control valve open lubricant passageway OPA.
Although in the above-described 6th embodiment, produce control gear 70 as an example of the electronic control valve of mechanical pressure controlled valve and electronic type example, but those skilled in the art should understand that control gear 70 can also adopt the device of other structures in addition.
The 6th mode of execution can also be achieved as follows beneficial effect except can realizing the beneficial effect of above-mentioned mode of execution.The oiling agent delivery volume of compression chamber can be controlled by control gear 70, thereby the oiling agent delivery volume that can reduce compression chamber in the time that compressor runs up to be to increase the performance of compressor, thereby and the oiling agent delivery volume that can increase compression chamber in the time of compressor low-speed running guarantee proper lubrication.
It should be appreciated by those skilled in the art that the corresponding beneficial effect that can be combined with to realize with moving scroll element 60,60A, 60B and the 60C of above-mentioned first to fourth mode of execution according to the structure of the main bearing seat 40E of the 6th mode of execution and control gear 70.Now, only the position of the lubricant entry 11 to the oiling agent supply passage OP in moving scroll element 60,60A, 60B and the 60C of first to fourth mode of execution is carried out suitable change and can be realized the object of controlling oiling agent delivery volume according to compressor operation state or motor rotary speed.
It should be appreciated by those skilled in the art that in the above-mentioned first to the 6th mode of execution, driving the motor of moving scroll element can be the inverter motor of variable speed.
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, it can comprise: determine scroll element, describedly determine scroll element and can comprise and determine vortex end plate and be formed on describedly to determine spiral helicine on vortex end plate and determine volution blade, moving scroll element, described moving scroll element can comprise moving vortex end plate, be formed on the spiral helicine moving volution blade of described moving vortex end plate the first side, be formed on the hub portion of described moving vortex end plate the second side and be formed in described second side of described moving vortex end plate and be positioned at the thrust surfaces of the radial outside of described hub portion, described moving volution blade and describedly determine volution blade and can be engaged with each other to form betwixt a series of compression chambers, the volume of described compression chamber reduces towards its radially inner side from the described radial outside of determining scroll element in respect to described process of determining scroll element translation rotation gradually at described moving scroll element, main bearing seat, the described hub portion that described main bearing seat can comprise the supporting portion of the thrust surfaces of moving scroll element described in axially support and receive described moving scroll element is to make the recess of described hub portion translation rotation therein, and oiling agent supply passage, near described oiling agent supply passage can be configured to that oiling agent is supplied to one of them compression chamber or its from described recess.
According to a second aspect of the invention, described oiling agent supply passage can be formed in the moving vortex end plate of described moving scroll element and described oiling agent supply passage can comprise lubricant entry and lubricant outlet, described lubricant entry can be formed on described second side of described moving vortex end plate, described lubricant outlet can be formed on described first side of described moving vortex end plate, can form the communicating passage that described lubricant entry and described lubricant outlet fluid are communicated with in described moving vortex end plate.
According to a third aspect of the present invention, the radially extension that described communicating passage can approximate horizontal.
According to a fourth aspect of the present invention, described communicating passage is tiltably extended.
According to a fifth aspect of the present invention, described communicating passage can be formed as the groove extending in described second side of described moving vortex end plate, described lubricant entry can be made up of the radial inner end of described groove, and described lubricant outlet can be formed as extending through described moving vortex end plate and arrive the radial outer end of described groove.
According to a sixth aspect of the invention, described oiling agent supply passage can further comprise the second lubricant outlet, described the second lubricant outlet can be formed on described first side of described moving vortex end plate and be arranged in described compression chamber another or its near.
According to a seventh aspect of the present invention, the internal diameter of supposing described recess is R, the turning radius of the translation rotation of described moving scroll element is r, distance between described lubricant entry and the central axis of described recess is a, and the radial position of described lubricant entry on described moving vortex end plate is designed so that above-mentioned parameter meets formula R-r<a<R+r.
According to an eighth aspect of the present invention, wherein suppose to determine line between lubricant entry described in scroll element translation rotation process and the central axis of described recess and be θ through the angle between the radial line of the central axis of described recess described, the maximum value of described angle is θ
max, the percentage of time that described lubricant entry is communicated with described recess be η
The target oiling agent delivery volume of wherein supplying with to described moving scroll element can be determined according to η.
According to a ninth aspect of the present invention, η is larger, and described target delivery volume is larger.
According to a tenth aspect of the present invention, the supporting portion of described main bearing seat can comprise the stayed surface contacting with the thrust surfaces of described moving scroll element, described stayed surface can in be formed with annular groove, described annular groove can be configured in the translation rotation process of described moving scroll element can with described lubricant entry intermittently fluid be communicated with, described annular groove can be communicated with described recess fluid via the roughly groove being radially arranged on described stayed surface.
According to an eleventh aspect of the present invention, the supporting portion of described main bearing seat can comprise the stayed surface contacting with the thrust surfaces of described moving scroll element, in described stayed surface, can be formed with annular groove, described annular groove can be configured in the translation rotation process of described moving scroll element can with described lubricant entry intermittently fluid be communicated with, described annular groove can be communicated with described annular groove fluid via the lubricant passageway being arranged in the main body portion of described main bearing seat.
According to a twelfth aspect of the present invention, in described lubricant passageway, can be provided with control gear, described control gear can be constructed to be permeable to optionally open or close described lubricant passageway.
According to the 13 aspect of the present invention, described control gear can be electronic control valve, described electronic control valve can be configured to open described lubricant passageway and close described lubricant passageway during in power-off in when energising, or described electronic control valve is opened described lubricant passageway can be configured at lubricant passageway described in closed in electrified state and in power-off time.
According to the 14 aspect of the present invention, described electronic control valve can be configured to control according to the operating condition of described scroll compressor.
According to the 15 aspect of the present invention, described electronic control valve be configured to according to the rotating speed of motor that drives described moving scroll element control make in the time that the rotating speed of described motor is more than or equal to predetermined value described in electronic control valve close described lubricant passageway and in the time that the rotating speed of described motor is less than described predetermined value described in electronic control valve open described lubricant passageway.
According to the 16 aspect of the present invention, described control gear can be pressure controlled valve, opens described lubricant passageway and close described lubricant passageway when the pressure that is subject at it is greater than described predetermined value when the pressure that described pressure controlled valve can be configured to be subject at it is less than or equal to predetermined value.
According to the 17 aspect of the present invention, described pressure controlled valve can comprise piston and for described piston provides the spring of bias force, described piston comprises fluid passage.
According to the 18 aspect of the present invention, described pressure controlled valve can be configured to: in the time that the pressure in described lubricant passageway is less than or equal to described predetermined value, fluid passage in described piston allows described lubricant passageway to be communicated with, and in the time that the pressure in described lubricant passageway is greater than described predetermined value, described piston is blocked described lubricant passageway.
According to nineteen of the present invention aspect, described lubricant entry can be configured to be positioned at all the time the surface-supported scope of the supporting portion of described main bearing seat in described moving scroll element translation rotation process.
According to the 20 aspect of the present invention, described scroll compressor can further comprise the live axle that drives described moving scroll element, described live axle can be supported and be comprised along the passage that roughly axial direction extends by described main bearing seat, the first end of described passage is communicated with described recess fluid, and the second end of described passage has been supplied to oiling agent.
According to the 21 aspect of the present invention, the second end of described passage can arrange feeding lubricating device.
According to the 22 aspect of the present invention, the target oiling agent delivery volume of supplying with to described moving scroll element can be determined according to the shape of described oiling agent supply passage or cross-section area.
According to the 23 aspect of the present invention, described one of them compression chamber can be the compression chamber of the outermost radial outside in described compression chamber.
According to the 24 aspect of the present invention, described scroll compressor can further comprise be configured to from by lubricant oil from described recess be supplied to described compression chamber another or its near the second oiling agent supply passage.
According to the 25 aspect of the present invention, described oiling agent supply passage can be configured so that described recess and described one of them compression chamber intermittently communicate with each other.
According to the 26 aspect of the present invention, described oiling agent supply passage can be configured so that described recess and described one of them compression chamber communicate with each other continuously.
According to the 27 aspect of the present invention, described scroll compressor can further comprise the motor that drives described moving scroll element, the inverter motor that described motor is variable speed.
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 (28)
1. a scroll compressor, comprising:
Determine scroll element (50), describedly determine scroll element and comprise and determine vortex end plate (54) and be formed on describedly to determine spiral helicine on vortex end plate and determine volution blade (56);
Moving scroll element (60, 60A, 60B, 60C, 60E), described moving scroll element comprises moving vortex end plate (64), be formed on the spiral helicine moving volution blade (66) of described moving vortex end plate the first side, be formed on the hub portion (62) of described moving vortex end plate the second side and be formed in described second side of described moving vortex end plate and be positioned at the thrust surfaces (68) of the radial outside of described hub portion, described moving volution blade (66) and describedly determine volution blade (56) and be engaged with each other to form betwixt a series of compression chamber (C1, C2, C3), the volume of described compression chamber reduces towards its radially inner side from the described radial outside of determining scroll element in respect to described process of determining scroll element translation rotation gradually at described moving scroll element,
Main bearing seat (40,40D, 40E), described main bearing seat comprises that the supporting portion (42) of thrust surfaces of moving scroll element described in axially support and the described hub portion (62) of the described moving scroll element of reception are to make the recess (46) of described hub portion translation rotation therein; And
Oiling agent supply passage (OP), near described oiling agent supply passage is configured to that oiling agent is supplied to one of them compression chamber (C1) or its from described recess (46).
2. scroll compressor as claimed in claim 1, wherein said oiling agent supply passage (OP) is formed in the moving vortex end plate (64) of described moving scroll element and described oiling agent supply passage (OP) comprises lubricant entry (11) and lubricant outlet (12), described lubricant entry (11) is formed on described second side of described moving vortex end plate (64), described lubricant outlet (12) is formed on described first side of described moving vortex end plate (64), in described moving vortex end plate (64), be formed with the communicating passage (13) that described lubricant entry (11) and described lubricant outlet (12) fluid are communicated with.
3. scroll compressor as claimed in claim 2, the radially extension of wherein said communicating passage (13) approximate horizontal.
4. scroll compressor as claimed in claim 2, wherein said communicating passage (13B) is extended obliquely.
5. scroll compressor as claimed in claim 2, wherein said communicating passage is formed as the groove (13A) extending in described second side of described moving vortex end plate (64), described lubricant entry (11) is made up of the radial inner end of described groove, and described lubricant outlet (12) is formed as extending through described moving vortex end plate (64) and arrives the radial outer end of described groove.
6. scroll compressor as claimed in claim 2, wherein said oiling agent supply passage (OP) also comprises the second lubricant outlet (12C), described the second lubricant outlet be formed on described first side of described moving vortex end plate (64) and be arranged in described compression chamber another or its near.
7. scroll compressor as claimed in claim 2, the internal diameter of wherein supposing described recess (46) is R, the turning radius of the translation rotation of described moving scroll element (60) is r, distance between the central axis of described lubricant entry (11) and described recess (46) is a, and the radial position of described lubricant entry (11) on described moving vortex end plate (64) is designed so that above-mentioned parameter meets formula R-r<a<R+r.
8. scroll compressor as claimed in claim 7, wherein suppose to determine line between lubricant entry (11) described in scroll element (60) translation rotation process and the central axis (O) of described recess (46) and be θ through the angle between the radial line (OA) of the central axis of described recess (46) described, the maximum value of described angle is θ
max, the percentage of time that described lubricant entry (11) is communicated with described recess (46) is η,
The target oiling agent delivery volume of wherein supplying with to described moving scroll element (60) is determined according to η.
9. scroll compressor as claimed in claim 8, wherein η is larger, and described target delivery volume is larger.
10. the scroll compressor as described in any one in claim 2-9, the supporting portion (42) of wherein said main bearing seat (40D) comprises the stayed surface (44) contacting with the thrust surfaces (68) of described moving scroll element (60), in described stayed surface (44), be formed with annular groove (47), described annular groove be configured in the translation rotation process of described moving scroll element (60) can with described lubricant entry (11) intermittently fluid be communicated with, described annular groove (47) is communicated with described recess (46) fluid via the roughly groove (48) being radially arranged on described stayed surface (44).
11. scroll compressors as described in any one in claim 2-6, the supporting portion (42) of wherein said main bearing seat (40E) comprises the stayed surface (44) contacting with the thrust surfaces (68) of described moving scroll element (60), in described stayed surface (44), be formed with annular groove (47), described annular groove be configured in the translation rotation process of described moving scroll element (60E) can with described lubricant entry (11) intermittently fluid be communicated with, described annular groove (47) is communicated with described recess (46) fluid via the lubricant passageway (OPA) being arranged in the main body portion of described main bearing seat (40E).
12. scroll compressors as claimed in claim 11 are wherein provided with control gear (70) in described lubricant passageway (OPA), and described control gear is constructed to be permeable to optionally open or close described lubricant passageway (OPA).
13. scroll compressors as claimed in claim 12, wherein said control gear (70) is electronic control valve, described electronic control valve is configured to open described lubricant passageway (OPA) and close described lubricant passageway (OPA) during in power-off in when energising, or described electronic control valve is opened described lubricant passageway (OPA) while being configured at lubricant passageway described in closed in electrified state (OPA) and in power-off.
14. scroll compressors as claimed in claim 13, wherein said electronic control valve is configured to control according to the operating condition of described scroll compressor.
15. scroll compressors as claimed in claim 14, wherein said electronic control valve be configured to according to the rotating speed of motor that drives described moving scroll element (60) control make in the time that the rotating speed of described motor is more than or equal to predetermined value described in electronic control valve close described lubricant passageway (OPA) and in the time that the rotating speed of described motor is less than described predetermined value described in electronic control valve open described lubricant passageway (OPA).
16. scroll compressors as claimed in claim 12, wherein said control gear (70) is pressure controlled valve (70), opens described lubricant passageway (OPA) and close described lubricant passageway (OPA) when the pressure that is subject at it is greater than described predetermined value when the pressure that described pressure controlled valve constitution Cheng Qi is subject to is less than or equal to predetermined value.
17. scroll compressors as claimed in claim 16, wherein said pressure controlled valve (70) comprises piston (72) and for described piston provides the spring (74) of bias force, described piston comprises fluid passage (73).
18. scroll compressors as claimed in claim 17, wherein, described pressure controlled valve (70) is configured to: in the time that the pressure in described lubricant passageway (OPA) is less than or equal to described predetermined value, fluid passage (73) in described piston (72) allows described lubricant passageway (OPA) to be communicated with, and in the time that the pressure in described lubricant passageway (OPA) is greater than described predetermined value, described piston (72) is blocked described lubricant passageway (OPA).
19. scroll compressors as claimed in claim 11, wherein said lubricant entry (11) is configured to be positioned at all the time the scope of the stayed surface (44) of the supporting portion (42) of described main bearing seat (40E) in described moving scroll element (60E) translation rotation process.
20. scroll compressors as claimed in any one of claims 1-9 wherein, further comprise the live axle (130) that drives described moving scroll element (60), described live axle is supported by described main bearing seat (40) and comprises along the passage (135) that roughly axial direction extends, the first end of described passage is communicated with described recess (46) fluid, and the second end of described passage has been supplied to oiling agent.
21. scroll compressors as claimed in claim 20, the second end of wherein said passage is provided with feeding lubricating device (138).
22. scroll compressors as described in any one in claim 1-6, the target oiling agent delivery volume of wherein supplying with to described moving scroll element (60) is determined according to shape or the cross-section area of described oiling agent supply passage (OPA).
23. scroll compressors as claimed in any one of claims 1-9 wherein, the compression chamber (C1) that wherein said one of them compression chamber is the outermost radial outside in described compression chamber.
24. scroll compressors as claimed in any one of claims 1-9 wherein, further comprise be configured to from by lubricant oil from described recess (46) be supplied to described compression chamber another or its near the second oiling agent supply passage (OP ').
25. scroll compressors as described in any one in claim 1-6, wherein said oiling agent supply passage (OP) is configured so that described recess (46) and described one of them compression chamber intermittently communicate with each other.
26. scroll compressors as claimed in any one of claims 1-9 wherein, wherein said oiling agent supply passage (OP) is configured so that described recess (46) and described one of them compression chamber communicate with each other continuously.
27. scroll compressors as described in claim 1-9, further comprise the motor (120) that drives described moving scroll element (46), the inverter motor that described motor is variable speed.
28. scroll compressors as claimed in claim 11, further comprise the motor (120) that drives described moving scroll element (46), the inverter motor that described motor is variable speed.
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| CN201210456871.5A CN103807166B (en) | 2012-11-14 | 2012-11-14 | Scroll compressor having a plurality of scroll members |
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| CN106194751A (en) * | 2015-05-05 | 2016-12-07 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| CN106415012A (en) * | 2014-06-11 | 2017-02-15 | 三菱电机株式会社 | Scroll compressor |
| CN107401509A (en) * | 2016-05-18 | 2017-11-28 | 艾默生环境优化技术(苏州)有限公司 | Oil supply device for compressor and compressor |
| CN107781160A (en) * | 2016-08-26 | 2018-03-09 | 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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| US10718330B2 (en) | 2017-02-06 | 2020-07-21 | Emerson Climate Technologies, Inc. | Co-rotating compressor with multiple compression mechanisms |
| US10995754B2 (en) | 2017-02-06 | 2021-05-04 | Emerson Climate Technologies, Inc. | Co-rotating compressor |
| CN112930442A (en) * | 2018-09-28 | 2021-06-08 | 艾默生环境优化技术有限公司 | Compressor oil management system |
| WO2021258585A1 (en) * | 2020-06-23 | 2021-12-30 | 艾默生环境优化技术(苏州)有限公司 | Scroll compression mechanism and scroll compressor |
| US11359631B2 (en) | 2019-11-15 | 2022-06-14 | Emerson Climate Technologies, Inc. | Co-rotating scroll compressor with bearing able to roll along surface |
| US11624366B1 (en) | 2021-11-05 | 2023-04-11 | Emerson Climate Technologies, Inc. | Co-rotating scroll compressor having first and second Oldham couplings |
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| EP4232715A4 (en) * | 2020-10-21 | 2024-04-03 | Emerson Climate Technologies | Compressor having lubrication system |
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