CN203362462U - Compressor system - Google Patents
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- CN203362462U CN203362462U CN 201320153166 CN201320153166U CN203362462U CN 203362462 U CN203362462 U CN 203362462U CN 201320153166 CN201320153166 CN 201320153166 CN 201320153166 U CN201320153166 U CN 201320153166U CN 203362462 U CN203362462 U CN 203362462U
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Abstract
The utility model relates to a compressor system (10A). The compressor system includes a first compressor (100) and a second compressor (200) connected in parallel with each other, a lubricant balancing conduit (500) disposed between the first compressor and the second compressor, a lubricant separator (A) connected with a discharge conduit (420) and supplying lubricant to the first compressor, and a first control valve (B) disposed in the lubricant balancing conduit. The first control valve is capable of selectively opening or closing the lubricant balancing conduit. The utility model discloses a compressor system can further improve the lubricated balanced and lower cost that has between two or many compressors.
Description
Technical field
The utility model relates to a kind of compressor assembly.
Background technique
The content of this part only provides the background information relevant to the disclosure, and it may not form prior art.
Known a kind of by two compressor assemblies that even more the multiple compressors parallel connection forms.The single compressor that this compressor assembly can utilize the multiple compressors of refrigerating capacity less to replace having larger refrigerating capacity, thus the cost of system and the operational efficiency that improves system reduced.In this compressor assembly consisted of the multiple compressors parallel connection, an important problem is the oiling agent balance between each compressor of assurance.Improve the oiling agent balance in this compressor assembly although proposed the whole bag of tricks,, particularly, when compressor assembly comprises variable displacement compressor, still there is improved space in the oiling agent balance in this compressor assembly.
Therefore, the compressor assembly that needs the oiling agent balance between a kind of each compressor further to improve.
The model utility content
The purpose of this utility model is to provide the compressor assembly that a kind of cost further reduces.
According to first aspect of the present utility model, a kind of compressor assembly is provided, comprising: the first compressor, described the first compressor comprises the first housing and is arranged on the first suction port and the first row gas port on described the first housing; And second compressor, described the second compressor comprises the second housing and is arranged on the second suction port and the second row gas port on described the second housing, described the first suction port and described the second suction port are via the admission line fluid communication with each other and be supplied to fluid via admission line, and described first row gas port and described second row gas port are discharged fluid via the exhaust duct fluid communication with each other and via exhaust duct; Described compressor assembly further comprises: lubricant separator, described lubricant separator is connected the oiling agent in the fluid of exhaust duct with separated flow with described exhaust duct, and described lubricant separator is supplied to described the first compressor via the oiling agent service by the isolated oiling agent of institute; The oiling agent equalizing main, described oiling agent equalizing main is arranged between described the first compressor and described the second compressor so that the oiling agent in described the first compressor can flow in described the second compressor via described oiling agent equalizing main; And first control valve, described the first control valve is arranged in the section be connected with described the first compressor of described oiling agent equalizing main and can be selectively opened or closes.
According to second aspect of the present utility model, be provided with the sensor for detection of the amounts of lubrication in described the first compressor in described the first compressor.
According to the third aspect of the present utility model, described sensor is liquid level sensor.
According to fourth aspect of the present utility model, described compressor assembly further comprises controlling component, and described controlling component is configured to control opening or closing of described the first control valve according to the survey data of described sensor.
According to the 5th aspect of the present utility model, described controlling component is configured to open described the first control valve when the survey data of described sensor is more than or equal to the first predetermined value, and close described the first control valve when the survey data of described sensor is less than or equal to the second predetermined value, described the first predetermined value is greater than described the second predetermined value.
According to the 6th aspect of the present utility model, described controlling component further is configured to open described the first control valve when the survey data of described sensor is more than or equal to described the first predetermined value and continued for first scheduled time, and closes described the first control valve when the survey data of described sensor is less than or equal to described the second predetermined value and continued for second scheduled time.
According to the 7th aspect of the present utility model, in described oiling agent service, be provided with the second control valve.
According to eight aspect of the present utility model, described controlling component further is configured to close described the second control valve when the survey data of described sensor is more than or equal to the 3rd predetermined value, and opens described the second control valve when the survey data of described sensor is less than or equal to the 4th predetermined value.
According to the 9th aspect of the present utility model, described the 3rd predetermined value is more than or equal to described the first predetermined value, and described the 4th predetermined value is less than or equal to described the second predetermined value.
According to the tenth aspect of the present utility model, described controlling component further is configured to close described the second control valve when the survey data of described sensor is more than or equal to described the 3rd predetermined value and continued for the 3rd scheduled time, and opens described the second control valve when the survey data of described sensor is less than or equal to described the 4th predetermined value and continued for the 4th scheduled time.
According to the tenth one side of the present utility model, described controlling component further is configured to logic control described second control valve contrary with described the first control valve.
According to the 12 aspect of the present utility model, described the first compressor is variable displacement compressor.
According to the tenth three aspects: of the present utility model, described the first compressor comprises moving scroll element, determines scroll element and capacity adjusting mechanism, and described capacity adjusting mechanism is configured so that describedly to determine scroll element and described moving scroll element is separated from each other in the axial direction or engages.
According to the 14 aspect of the present utility model, described the first compressor is frequency-changeable compressor.
According to the 15 aspect of the present utility model, described the first compressor comprises moving scroll element and determines scroll element, described moving scroll element and describedly determine between scroll element to form the compression chamber that a series of volumes reduce to radially inner side gradually from radial outside, be formed with at least one in determining scroll element at the pressure release passage that provides fluid to be communicated with between suction pressure region and one of them compression chamber described, in described pressure release passage, be provided with can be selectively opened the 3rd control valve.
According to the 16 aspect of the present utility model, described the first compressor is fixed-capacity compressor.
According to the 17 aspect of the present utility model, described the second compressor is fixed-capacity compressor.
According to the tenth eight aspect of the present utility model, described the first compressor and described the second compressor are scroll compressor.
According to the 19 aspect of the present utility model, the group that described the first compressor selects free piston compressor, rotor-type compressor, screw compressor, centrifugal compressor to form, the group that described the second compressor selects free piston compressor, rotor-type compressor, screw compressor, centrifugal compressor to form.
According to the 20 aspect of the present utility model, the compressor that described the first compressor and described the second compressor are same type.
According to the 20 one side of the present utility model, described the first compressor and described the second compressor are dissimilar compressor.
According to the 22 aspect of the present utility model, first section be connected with described the first compressor of described admission line is configured to the fluid resistance that provides less than second section be connected with described the second compressor of described admission line.
According to the 20 three aspects: of the present utility model, at least one item in the angle of the length by selecting described the first section and described the second section, cross-section area, bending, the quantity of bending makes the fluid resistance of described the first section be less than the fluid resistance of described the second section.
According to the 24 aspect of the present utility model, described compressor assembly further comprises the 3rd compressor, the 3rd suction port of described the 3rd compressor is communicated with the first suction port of described the first compressor and the second suction port fluid of described the second compressor respectively via described admission line, the 3rd relief opening of described the 3rd compressor is communicated with the first row gas port of described the first compressor and the second row gas port fluid of described the second compressor respectively via described exhaust duct, and described the 3rd compressor is communicated with described the first compressor and described the second compressor fluid via described oiling agent equalizing main.
According to the 25 aspect of the present utility model, between described the second compressor and described the 3rd compressor, be provided with the gas equalizing main.
According to the 26 aspect of the present utility model, in described oiling agent service, be provided with throttle element.
According to the 27 aspect of the present utility model, described throttle element is capillary tube.
According to the 20 eight aspect of the present utility model, described the first compressing mechanism causes to have than the lower pressure of inspiration(Pi) of described the second compressor.
Adopt compressor assembly of the present utility model, can be in the situation that realize in system that the oiling agent balance reduces the quantity of required sensor and control valve, thus can further reduce the cost of whole system.
The 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 utility model will become, wherein:
Fig. 1 is a kind of schematic diagram of compressor assembly of routine;
Fig. 2 is the schematic cross sectional views of the compressor in compressor assembly shown in Fig. 1;
Fig. 3 is the schematic cross sectional views of the compressor of another in compressor assembly shown in Fig. 1;
Fig. 4 is the schematic diagram according to the compressor assembly of a kind of mode of execution of the utility model;
Fig. 5 is the schematic piping arrangement according to the compressor assembly of a kind of mode of execution of the utility model; And
Fig. 6 is the schematic diagram of determining scroll element that another kind has the capacity regulating function.
Embodiment
Following description related to the preferred embodiment is only exemplary, and is never the restriction to the utility model and application or usage.In each accompanying drawing, adopt identical reference character to mean identical parts, so the structure of same parts will no longer be repeated in this description.
At first essential structure and the principle of conventional compressor assembly are described with reference to Fig. 1-3.
As shown in Figure 1, compressor assembly 10 comprises the first compressor 100, the second compressor 200, the 3rd compressor 300.The first compressor 100, the second compressor 200 and the 3rd compressor 300 are connected in parallel with each other to form so-called multi-connected machine system.More specifically, the first compressor 100 can comprise the first housing 110 and be arranged on the first suction port 118 and the first row gas port 119 on the first housing 110.The first housing 110 stores oiling agent interior can comprising in the first suction pressure region and first row atmospheric pressure district (back specifically describes with reference to Fig. 2) and the first housing 110.In the structure of this vertical compressor, oiling agent is stored in the bottom section of the first housing 110 usually.Similarly, the second compressor 200 comprises the second housing 210 and is arranged on the second suction port 218 and the second row gas port 219 on the second housing 210.The second housing 210 stores oiling agent interior can comprising in the second suction pressure region and second row atmospheric pressure district (back specifically describes with reference to Fig. 3) and the second housing 210.The 3rd compressor 300 can have the structure identical with the second compressor 200.Particularly, the 3rd compressor 300 can comprise the 3rd housing 310 and be arranged on the 3rd suction port 318 and the 3rd relief opening 319 on the 3rd housing 310.The first suction port 118, the second suction port 218 and the 3rd suction port 318 are via admission line 410 fluid communication with each other and be supplied to fluid via admission line 410.First row gas port 119, second row gas port 219 and the 3rd relief opening 319 are discharged fluid via exhaust duct 420 fluid communication with each other and via exhaust duct 420.
More specifically, the 3rd air inlet that admission line 410 can comprise that the first air inlet be connected with the first suction port 118 is in charge of 412, the second air inlet of being connected with the second suction port 218 is in charge of 414, be connected with the 3rd suction port 318 is in charge of 416 and the first air inlet is in charge of to the 412, second air inlet and is in charge of the 414 and the 3rd air inlet and is in charge of 416 intake manifolds that link together 418.Air inlet in compressor assembly 10 (suction fluid) can suck via intake manifold 418, then is in charge of the 412, second air inlet via the first air inlet respectively and is in charge of the 414 and the 3rd air inlet and is in charge of 416 suction the first compressors 100, the second compressor 200 and the 3rd compressor 300.Similarly, exhaust duct 420 can comprise the first exhaust charge 422 be connected with first row gas port 119, the second exhaust charge 424 be connected with second row gas port 219, the 3rd exhaust charge 426 be connected with the 3rd relief opening 319 and the exhaust manifold 428 that the first exhaust charge 422, the second exhaust charge 424 and the 3rd exhaust charge 426 are linked together.The first compressor 100, the second compressor 200 with the fluid after compression in the 3rd compressor 300, via the first exhaust charge 422, the second exhaust charge 424 and the 3rd exhaust charge 426, discharge respectively and in exhaust manifold 428, converging with together be discharged to compressor assembly 10.
Be provided with oiling agent equalizing main 500 with to each compressor supply of lubricant and/or make oiling agent in each compressor to flow mutually via oiling agent equalizing main 330 between the first compressor 100, the second compressor 200 and the 3rd compressor 300.For example, oiling agent equalizing main 500 can be respectively be arranged on the first compressor 100 in oiling agent balance port 117, be arranged on the oiling agent balance port 217 in the second compressor 200 and the oiling agent balance port 317 that is arranged in the 3rd compressor 300 is connected.In addition, the section 510 of oiling agent equalizing main 500 can also with compressor assembly 10 in lubricant separator A(for example, as shown in Figure 5) fluid is communicated with to each compressor supply of lubricant.
Be respectively arranged with the sensor 531,532 and 533 for detection of the amounts of lubrication in each compressor on the first compressor 100, the second compressor 200 and the 3rd compressor 300.Be respectively arranged with control valve 541,542 and 543 near oiling agent balance port 117,217 and 317.The controlling component of compressor assembly (for example, control circuit board or electronic control unit (ECU) etc.) can control respectively opening or closing of each control valve 541,542 and 543 according to the measurement result of each sensor 531,532 and 533, thus adjust the amounts of lubrication in each compressor.
The following while is with reference to Fig. 2 and 3, take variable capacity scroll compressor and fixed capacity scroll compressor more specifically to describe the concrete structure of compressor assembly 10 as example.
Fig. 2 shows a kind of example of scroll compressor of fixed capacity of routine.The second compressor 200 or the 3rd compressor 300 in Fig. 1 can adopt the compressor of constructing shown in Fig. 2, but are not limited to this.Second compressor 200 of below take is example, specifically describes the structure of this compressor 200.The second housing 210 that the housing 210(of scroll compressor shown in Fig. 2 200 is above-mentioned) comprise body 211 cylindraceous roughly, be arranged on body 211 1 ends top cover 212, be arranged on the bottom 214 of body 211 the other ends.Be provided with dividing plate 216 and be separated into high pressure side (that is, exhaust pressure district) and low voltage side (that is, suction pressure region) with the inner space by compressor between top cover 212 and body 211.Form high pressure side between dividing plate 216 and top cover 212, and form low voltage side between dividing plate 216, body 211 and bottom 214.Be provided with the suction port 218 for sucking fluid in low voltage side, be provided with the relief opening 219 for the fluid after discharging compression in high pressure side.Although relief opening 219 is depicted as the center of top that is arranged on top cover 212 in Fig. 2, it will be appreciated by those skilled in the art that relief opening 219 also can be arranged on the side of top cover 212 as shown in Figure 1.Be provided with the motor 220 formed by stator 222 and rotor 224 in housing 210.Be provided with live axle 230 in rotor 224 to drive the compressing mechanism formed by determining scroll element 250 and moving scroll element 260.Moving scroll element 260 comprises end plate 264, be formed on the hub section 262 of end plate one side and be formed on the spiral helicine blade 266 of end plate opposite side.Determining scroll element 250 comprises end plate 254, is formed on the spiral helicine blade 256 of end plate one side and is formed on the exhaust port 252 of the substantial middle position of end plate.Form the compression chamber that a series of volumes reduce to radially inner side gradually from radial outside between the volution blade 266 of the volution blade 256 of determining scroll element 250 and moving scroll element 260.Wherein, the compression chamber of outermost radial outside is in pressure of inspiration(Pi), and radially the most inboard compression chamber is in exhaust pressure.Middle compression chamber between pressure of inspiration(Pi) and exhaust pressure, thereby also be referred to as middle pressure chamber.
One side of moving scroll element 260 is supported by the top (this part forms the thrust member) of main bearing seat 240, and the main bearing 244 of an end of live axle 230 in being arranged on main bearing seat 240 supports.One end of live axle 230 is provided with eccentric crank pin 232, is provided with unloading lining 242 between the hub section 262 of eccentric crank pin 232 and moving scroll element 260.Driving by motor 220, moving scroll element 260 will be with respect to determining scroll element 250 translation rotations (, the central axis of moving scroll element 260 is around the central axis rotation of determining scroll element 250, but moving scroll element 260 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 of determining to arrange between scroll element 250 and moving scroll element 260.Fluid after determining scroll element 250 and 260 compressions of moving scroll element is discharged to high pressure side by exhaust port 252.In order to prevent that on high-tension side fluid is back to low voltage side via exhaust port 252 under specific circumstances, one-way valve or outlet valve 270 can be set at exhaust port 252 places.
In order to realize the compression of fluid, determining must effective sealing between scroll element 250 and moving scroll element 260.On the one hand, determine between the end plate 264 of the distal portion of volution blade 256 of scroll element 250 and moving scroll element 260 and the distal portion of the volution blade 266 of moving scroll element 260 and determine to need axial seal between the end plate 254 of scroll element 250.
Usually, the side contrary with volution blade 256 at the end plate 254 of determining scroll element 250 is provided with back pressure cavity 258.Be provided with black box 280 in back pressure cavity 258, the axial displacement of black box 280 is subject to the restriction of dividing plate 216.Thereby being communicated with middle pressure chamber fluid to form by the axially extended through hole (not shown) formed in end plate 254, back pressure cavity 258 will determine the power that scroll element 250 is pressed towards moving scroll element 260.Due to a side of moving scroll element 260 upper support by main bearing seat 240, so utilize pressure in back pressure cavity 258 can be effectively will to determine scroll element 250 and moving scroll element 260 forces together.When the pressure in each compression chamber surpasses setting value, thus the pressure in these compression chambers produce will make and determine scroll element 250 and move upward over the downforce provided in back pressure cavity 258 with joint efforts.Now, fluid in compression chamber by the distal portion of the volution blade 266 of the gap between the end plate 264 of the distal portion of the volution blade 256 by determining scroll element 250 and moving scroll element 260 and moving scroll element 260 and determine clearance leakage between the end plate 254 of scroll element 250 to low voltage side to realize unloading, thereby provide axial elasticity for scroll compressor.
On the other hand, determine also to need radial seal between the side surface of volution blade 266 of the side surface of volution blade 256 of scroll element 250 and moving scroll element 260.This radial seal between the two driving force that the centrifugal force in operation process and live axle 230 provide by means of moving scroll element 260 usually realizes.Particularly, in operation process, by the driving of motor 220, moving scroll element 260 will, with respect to determining scroll element 250 translation rotations, will produce centrifugal force thereby move scroll element 260.On the other hand, the eccentric crank pin 232 of live axle 230 also can produce the driving force component that contributes to realize determining scroll element and moving scroll element radial seal in rotary course.The volution blade 266 of moving scroll element 260 will abut on the volution blade 256 of determining scroll element 250 by means of above-mentioned centrifugal force and driving force component, thereby realize the radial seal between the two.When incompressible material (such as solid impurity, lubricant oil and liquid refrigerant) enters in compression chamber and is stuck between volution blade 256 and volution blade 266, volution blade 256 and volution blade 266 can temporarily radially be separated from each other to allow foreign matter to pass through, and have therefore prevented that volution blade 256 or 266 from damaging.This ability that can radially separate provides radial compliance for scroll compressor, has improved the reliability of compressor.
In compressor 200 operation process, the oiling agent that is stored in housing 210 bottoms can be supplied to the end of eccentric crank pin 232 and under the effect of gravity and in the effect current downflow of centrifugal force with splash and be lubricated with cooling with other movable parts in compressor via the oil supply gallery 233 formed in live axle 230.
Fig. 3 shows a kind of variable-displacement scroll compressor of routine.The first compressor 100 in Fig. 1 can adopt the structure of the compressor shown in Fig. 3, but is not limited to this.Essential structure and the scroll compressor shown in Fig. 2 200 of the scroll compressor 100 shown in Fig. 3 are roughly the same.Briefly, the first above-mentioned housing 110 of the housing 110(of scroll compressor 100) comprise roughly body 111 cylindraceous, top cover 112 and bottom 114.Be provided with dividing plate 116 and be separated into high pressure side (that is, exhaust pressure district) and low voltage side (that is, suction pressure region) with the inner space by compressor between top cover 112 and body 111.Form high pressure side between dividing plate 116 and top cover 112, and form low voltage side between dividing plate 116, body 111 and bottom 114.Be provided with suction port 118(for sucking fluid referring to Fig. 1 in low voltage side, not shown in Fig. 3), be provided with relief opening 119(for the fluid after discharging compression in high pressure side referring to Fig. 1, not shown in Fig. 3).Be provided with the motor 120 formed by stator 122 and rotor 124 in housing 110.Be provided with live axle 130 in rotor 124 to drive the compressing mechanism formed by determining scroll element 150 and moving scroll element 160.Moving scroll element 160 comprises end plate 164, be formed on the hub section 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 exhaust port 152 of the substantial middle position of end plate.One side of moving scroll element 160 is supported by the top (this part forms the thrust member) of main bearing seat 140, and the main bearing 144 of an end of live axle 130 in being arranged on main bearing seat 140 supports.One end of live axle 130 is provided with eccentric crank pin 132, is provided with unloading lining 142 between the hub section 162 of eccentric crank pin 132 and moving scroll element 160.A side contrary with volution blade 156 at the end plate 154 of 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.In compressor 100 operation process, the oiling agent that is stored in housing 110 bottoms can be supplied to the end of eccentric crank pin 132 and under the effect of gravity and in the effect current downflow of centrifugal force with splash and be lubricated with cooling with other movable parts in compressor via the oil supply gallery 133 formed in live axle 130.
Variable-displacement scroll compressor 100 shown in Fig. 3 further comprises capacity adjusting mechanism 190, and it is configured to determine scroll element 150 and moving scroll element 160 is separated from each other or engages on the axial direction of compressor 100.More specifically, capacity adjusting mechanism 190 can comprise and determine piston 192 that scroll element 150 is connected and the fixing cylinder body 194 with respect to housing 110.Thereby piston 192 can drive and determine scroll element 150 motion in the axial direction together in the interior slip of cylinder body 194.Space S between the end face of piston 192 and cylinder body 194 can be via the passage formed on the passage 193(in piston 192 or cylinder body 194) with the exhaust pressure district fluid of compressor 100, be communicated with.In addition, the space S between the end face of piston 192 and cylinder body 194 can also be communicated with suction pressure region or admission line 410 fluids of compressor 100 via joint 195.The capacity regulating control valve can be set in the pipeline between joint 195 and suction pressure region or admission line 410 to be communicated with the fluid between suction pressure region to control space S.
Capacity adjusting mechanism shown in Fig. 3 is described in detail in disclosed patent documentation CN100460683C the applicant's, and the full content of the document is incorporated to this paper by reference.
Adopting in the compressor assembly 10 that as above compressor 100,200 and 300 forms, for example working as compressor 100,200 and 300 and have in the situation of same capability (being 100%), whole compressor assembly 10 can provide from 0% to 300% capacity regulating.For example, when the first compressor 100 running and the second compressor 200 and the 3rd compressor 300 while stopping, compressor assembly 10 can be realized 0% to 100% capacity regulating; When the first compressor 100 with the second compressor 200 all turns round and the 3rd compressor 300 while stopping, compressor assembly 10 can be realized 100% to 200% capacity regulating; When the first compressor 100, the second compressor 200 and the 3rd compressor 300 all turn round, compressor assembly 10 can be realized 200% to 300% capacity regulating.It will be understood by those skilled in the art that all right further fixed capacity or variable-displacement compressor in parallel in compressor assembly 10, or can only be formed by the first compressor 100 and the second compressor 200.Thereby as above the compressor assembly of structure can be realized the modulation of capacity more flexibly, larger total capacity and lower cost.
Yet, in this compressor assembly 10, need to use 531,532,533 and three control valves 541,542,543 of three sensors corresponding with the number of compressors in compressor assembly regulate and each compressor of balance between amounts of lubrication, therefore the cost of whole compressor assembly is relatively high.In addition, also more complicated of the control logic between each control valve 541,542,543.
Next referring to Figure 4 and 5, the compressor assembly 10A according to the utility model mode of execution is described.The essential structure of compressor assembly 10A and the essential structure of the compressor assembly shown in Fig. 1 10 are roughly the same, and therefore in Fig. 4, adopt identical reference character refer to identical parts and will omit illustrating of these parts.
In the compressor assembly 10A according to a kind of mode of execution of the present utility model, comprise three compressors that are connected in parallel with each other, i.e. the first compressor 100, the second compressor 200 and the 3rd compressor 300, to form so-called multi-connected machine system.It should be appreciated by those skilled in the art that according to compressor assembly 10A of the present utility model and also can only comprise the compressor of two parallel connections, i.e. the first compressor 100 and the second compressor 200, or can comprise the compressor of more parallel connection.The suction port of each compressor can have fluid via shared admission line 410 fluid communication with each other and supply, and the relief opening of each compressor can and be discharged fluid via shared exhaust duct 420 fluid communication with each other.Compressor assembly 10A further comprises the lubricant separator A be connected with shared exhaust duct 420, the oiling agent with separated flow in the fluid of exhaust duct 420.Communicate with each other via shared oiling agent equalizing main 500 between each compressor 100,200 and 300, flow in the second compressor 200 and/or the 3rd compressor 300 via oiling agent equalizing main 500 to allow the oiling agent in the first compressor 100.
According in compressor assembly 10A of the present utility model, lubricant separator A only is supplied to the first compressor 100 via oiling agent service 700 by the isolated oiling agent of institute.Particularly, according in compressor assembly 10A of the present utility model, for detection of the sensor H(of amounts of lubrication for example can only on the first compressor 100, be provided with, corresponding to the sensor 531 shown in Fig. 1), and can omit the sensor for detection of amounts of lubrication on the second compressor 200 and the 3rd compressor 300.At this, sensor H can be liquid level sensor, but is not limited to this.In addition, in compressor assembly 10A, can only in the section be connected with the first compressor 100 of oiling agent equalizing main 500, the first control valve B(be set for example, corresponding to the control valve 541 shown in Fig. 1) optionally to open or close oiling agent equalizing main 500.Further, the second control valve J can be set in oiling agent service 700, with optionally from lubricant separator A to the first compressor 100 supply of lubricant.
The first control valve B and the second control valve J can be solenoid valve, but are not limited to this.Can be by the controlling component 800(such as control circuit board or electronic control unit (ECU) in compressor assembly 10A referring to Fig. 5) control the first control valve B and/or the second control valve J to realize the oiling agent balance of expectation.In other words, controlling component 800 can be controlled opening, close or aperture of the first control valve B and/or the second control valve J according to the survey data of sensor H.
More specifically, in whole compressor assembly 10A, total amounts of lubrication is certain.Each compressor 100,200 all can separate and be stored in lubricant separator A by lubricated dose of separator A with contained oiling agent in 300 exhaust.Due in lubricant separator A for the oiling agent memory block in the housing of exhaust pressure compressor 100 is pressure of inspiration(Pi), so the oiling agent in lubricant separator A can be in the effect current downflow of pressure reduction in the first compressor 100.Can open the first control valve B when the amounts of lubrication in the first compressor 100 reaches certain value, thereby make oiling agent in the first compressor 100 can be under the effect of gravity flow in other compressors 200 and/or 300 with to other compressor supplemental lubrication agent via oiling agent equalizing main 500.
More specifically, controlling component 800 can be configured to open the first control valve B when the survey data of sensor H is more than or equal to the first predetermined value to allow to other compressor supply of lubricant, and closes the first control valve B to stop the oiling agent supply to other compressors when the survey data of sensor H is less than or equal to the second predetermined value.The first predetermined value can be set for and be greater than the second predetermined value.
Due to the fluctuation of the oiling agent in the first compressor etc., authenticity for the survey data that guarantees sensor H, controlling component can further be configured to for example, open the first control valve B when the survey data of sensor H is more than or equal to the first predetermined value and continues first scheduled time (5 seconds), and for example, closes the first control valve B when the survey data of sensor is less than or equal to the second predetermined value and continues second scheduled time (can be also 5 seconds).
In addition, controlling component 800 can further be configured to close the second control valve J when the survey data of sensor H is more than or equal to the 3rd predetermined value and supply with the oiling agent stopped from lubricant separator A to the first compressor 100, and opens the second control valve J and supply with the oiling agent started from lubricant separator A to the first compressor 100 when the survey data of sensor H is less than or equal to the 4th predetermined value.The 3rd predetermined value can be more than or equal to the first predetermined value, and the 4th predetermined value can be less than or equal to the second predetermined value.
Similarly, authenticity for the survey data that guarantees sensor H, controlling component 800 can be configured to be more than or equal to the 3rd predetermined value and continue the 3rd predetermined second control valve J that closes constantly in the survey data of sensor H, and opens the second control valve J when the survey data of sensor H is less than or equal to the 4th predetermined value and continued for the 4th scheduled time.
Above-mentioned parameters: the first predetermined value, the second predetermined value, the 3rd predetermined value, the 4th predetermined value, first scheduled time, second scheduled time, the 3rd scheduled time and the 4th scheduled time more can preset according to the concrete property of compressor 100 and compressor assembly 10A and Operation Conditions etc.
More simplifiedly, controlling component 800 can be configured to the logic control second control valve J contrary with the first control valve B.That is, controlling component 800 can be configured to close the second control valve J when the first control valve B opens, and opens the second control valve J when the first control valve B closes.Thereby, can simplify further the control logic of each control valve.
On the other hand, when the first compressor 100 is the variable-displacement compressor shown in Fig. 3, due to compressor during in unloaded state the compressing mechanism in compressor can not produce fluid pumping effect (causing pressure decreased), so even the pressure of inspiration(Pi) of each compressor is identical, the pressure of the suction pressure region of variable displacement compressor in fact also can be slightly lower than the pressure of the suction pressure region of fixed-capacity compressor.In this case, when control valve B opens, the oiling agent in the first compressor 100 can be in the two effect current downflow of gravity and pressure reduction in other compressors 200 and 300.
In addition, during the compressor that is the fixed capacity shown in Fig. 2 at the first compressor 100, first section be connected with the first compressor 100 of admission line 410 can be configured to provide than admission line 410 with the second compressor 200(and/or the 3rd compressor 300) fluid resistance that the second section of being connected is less.For example, at least one item in the angle of length that, can be by selecting the first section and the second section, cross-section area, bending, the quantity of bending makes the fluid resistance of the first section be less than the fluid resistance of the second section.In this case, in the situation that the pressure of inspiration(Pi) of compressor assembly 10A is identical, because the fluid resistance of the first section from fluid to the first compressor 100 that supply with is little, so the pressure of the suction pressure region in the first compressor 100 in fact will be slightly higher than the pressure of the suction pressure region in other compressors.So, when the first control valve B opens, the oiling agent in the first compressor 100 not only can but also can be supplied to other compressors 200,300 from the first compressor 100 under the effect poor at the pressure of inspiration(Pi) of each compressor under the effect of gravity.Thereby, further guaranteed that the oiling agent of other compressors is supplied with.It should be appreciated by those skilled in the art that and above-mentionedly realize that by the parameter of revising the first section and the second section the technological means of the variation of fluid resistance also can be in conjunction with being applied to the first compressor 100 for the situation of variable displacement compressor.Perhaps, more broadly, no matter the first compressor 100 is fixed-capacity compressor or variable displacement compressor, the first compressor 100 can adopt any mode and be configured with than the lower pressure of inspiration(Pi) of the second compressor 200.
In addition, in order to make oiling agent, between the second compressor 200 and the 3rd compressor 300, distribute more equably, can between the second compressor 200 and the 3rd compressor 300, gas equalizing main 600 be set.
The compressor assembly 10A of above-mentioned structure can have following beneficial effect and distortion.
The first compressor 100 can be variable displacement compressor, can be also fixed-capacity compressor.In the situation that the two, owing to can in compressor assembly, only with a sensor H and a control valve B, realizing oiling agent supply and/or the balance between each compressor, so reduced the cost and the control logic of having simplified system of whole system.In addition, in the situation that the first compressor 100 is variable displacement compressors, because at first the oiling agent in lubricant separator A is supplied to the first compressor 100, so preferentially guaranteed the oiling agent supply of the first compressor 100 that cost is relatively high, thereby reduced the possibility that the first compressor 100 breaks down or damages.
In the situation that the first compressor 100 is variable displacement compressor, the first compressor 100 can adopt making shown in Fig. 3 to determine the variable displacement mechanism 190 that scroll element 150 and moving scroll element 160 are separated from each other in the axial direction or engage.But the first compressor 100 also can use the variable displacement compressor of other types.For example, the first compressor 100 can be frequency-changeable compressor, in this compressor, can realize by the rotating speed that changes motor the adjusting of capacity.Again for example, referring to Fig. 6, at least one pressure release passage 153 that provides fluid to be communicated with between suction pressure region and one of them compression chamber can be provided for the determining in scroll element 150A of the first compressor 100, can in pressure release passage 153, arrange can be selectively opened control valve 155.When control valve 155 is closed, all compression chambers carry out squeeze operation, and when control valve 155 is opened, thereby a part of compression chamber is allowed with the part capacity by the pressure release compressor.Capacity regulating shown in Fig. 6 is configured in being described in detail in disclosed Chinese utility model patent CN2027487U of the applicant, does not repeat them here.The full content of document CN2027487U is incorporated to this paper by reference.
In addition, in the above-described embodiment, compressor assembly 10A comprises three compressors, but those skilled in the art should understand that compressor assembly 10A can comprise two or more than the compressor of three to realize still less or more total capacity.
In addition, in the above-described embodiment, adopted control valve J to control the opening and closing of oiling agent service 700.But, in other embodiments, can use such as throttle element capillaceous and replace control valve J.In this case, the oiling agent in lubricant separator A can be supplied to the first compressor 100 via throttle element always.Can select in advance the optimum aperture of throttle element by modes such as tests.Control valve B still can be controlled to open or close by above-mentioned control logic.Adopt this mode, can further reduce the cost of compressor assembly and simplify control logic.
In addition, in the above-described embodiment, it is scroll compressor that the first compressor 100, the second compressor 200 and the 3rd compressor 300 are depicted as, but those skilled in the art should understand that the group that these compressors can select respectively free piston compressor, rotor-type compressor, screw compressor, centrifugal compressor to form.In addition, the first compressor and the second compressor (or the 3rd compressor) can be the compressor of same type, can be also dissimilar compressor, to realize system layout more flexibly.
Although described various mode of execution of the present utility model in detail at this, but should be appreciated that the utility model is not limited to the embodiment of describing in detail and illustrating here, in the situation that do not depart from essence of the present utility model and scope can be realized by those skilled in the art other modification and variant.All these modification and variant all fall in scope of the present utility model.And all members described here can be replaced by the member be equal on other technologies.
Claims (28)
1. a compressor assembly (10A) comprising:
The first compressor (100), described the first compressor (100) comprises the first housing (110) and is arranged on the first suction port (118) and the first row gas port (119) on described the first housing (110); And
The second compressor (200), described the second compressor (200) comprises the second housing (210) and is arranged on the second suction port (218) and the second row gas port (219) on described the second housing (210), described the first suction port (118) and described the second suction port (218) have been supplied to fluid via admission line (410) fluid communication with each other and via admission line (410), described first row gas port (119) and described second row gas port (219) are discharged fluid via exhaust duct (420) fluid communication with each other and via exhaust duct (420),
It is characterized in that described compressor assembly (10A) further comprises:
Lubricant separator (A), described lubricant separator (A) is connected the oiling agent in the fluid of exhaust duct (420) with separated flow with described exhaust duct (420), and described lubricant separator (A) is supplied to described the first compressor (100) via oiling agent service (700) by the isolated oiling agent of institute;
Oiling agent equalizing main (500), described oiling agent equalizing main (500) is arranged between described the first compressor (100) and described the second compressor (200) so that the oiling agent in described the first compressor (100) can flow in described the second compressor (200) via described oiling agent equalizing main (500); And
The first control valve (B), described the first control valve (B) is arranged in the section be connected with described the first compressor (100) of described oiling agent equalizing main (500) and can be selectively opened or closes.
2. compressor assembly as claimed in claim 1, be provided with the sensor (H) for detection of the amounts of lubrication in described the first compressor (100) in wherein said the first compressor (100).
3. compressor assembly as claimed in claim 2, wherein said sensor (H) is liquid level sensor.
4. compressor assembly as claimed in claim 2, further comprise controlling component (800), and described controlling component is configured to control opening or closing of described the first control valve (B) according to the survey data of described sensor (H).
5. compressor assembly as claimed in claim 4, wherein said controlling component (800) is configured to open described the first control valve (B) when the survey data of described sensor (H) is more than or equal to the first predetermined value, and close described the first control valve (B) when the survey data of described sensor (H) is less than or equal to the second predetermined value, described the first predetermined value is greater than described the second predetermined value.
6. compressor assembly as claimed in claim 5, wherein said controlling component (800) further is configured to open described the first control valve (B) when the survey data of described sensor (H) is more than or equal to described the first predetermined value and continued for first scheduled time, and closes described the first control valve (B) when the survey data of described sensor (H) is less than or equal to described the second predetermined value and continued for second scheduled time.
7. compressor assembly as claimed in claim 5 wherein is provided with the second control valve (J) in described oiling agent service (700).
8. compressor assembly as claimed in claim 7, wherein, described controlling component (800) further is configured to close described the second control valve (J) when the survey data of described sensor (H) is more than or equal to the 3rd predetermined value, and opens described the second control valve (J) when the survey data of described sensor (H) is less than or equal to the 4th predetermined value.
9. compressor assembly as claimed in claim 8, wherein, described the 3rd predetermined value is more than or equal to described the first predetermined value, and described the 4th predetermined value is less than or equal to described the second predetermined value.
10. compressor assembly as claimed in claim 8, wherein, described controlling component (800) further is configured to close described the second control valve (J) when the survey data of described sensor (H) is more than or equal to described the 3rd predetermined value and continued for the 3rd scheduled time, and opens described the second control valve (J) when the survey data of described sensor (H) is less than or equal to described the 4th predetermined value and continued for the 4th scheduled time.
11. compressor assembly as claimed in claim 7, wherein, described controlling component (800) further is configured to logic control described second control valve (J) contrary with described the first control valve (B).
12. compressor assembly as described as any one in claim 1-11, wherein said the first compressor (100) is variable displacement compressor.
13. compressor assembly as claimed in claim 12, wherein said the first compressor (100) comprises moving scroll element (160), determines scroll element (150) and capacity adjusting mechanism (190), and described capacity adjusting mechanism (190) is configured so that describedly to determine scroll element (150) and described moving scroll element (160) is separated from each other in the axial direction or engages.
14. compressor assembly as described as any one in claim 1-11, wherein said the first compressor (100) is frequency-changeable compressor.
15. compressor assembly as described as any one in claim 1-11, wherein said the first compressor (100) comprises moving scroll element (160) and determines scroll element (150), described moving scroll element (160) and describedly determine between scroll element (150) to form the compression chamber that a series of volumes reduce to radially inner side gradually from radial outside, be formed with at least one in determining scroll element (150) at the pressure release passage (153) that provides fluid to be communicated with between suction pressure region and one of them compression chamber described, in described pressure release passage (153), be provided with can be selectively opened the 3rd control valve (155).
16. compressor assembly as described as any one in claim 1-11, wherein said the first compressor (100) is fixed-capacity compressor.
17. compressor assembly as described as any one in claim 1-11, wherein said the second compressor (200) is fixed-capacity compressor.
18. compressor assembly as described as any one in claim 1-11, wherein said the first compressor (100) and described the second compressor (200) are scroll compressor.
19. compressor assembly as described as any one in claim 1-11, the group that wherein said the first compressor (100) selects free piston compressor, rotor-type compressor, screw compressor, centrifugal compressor to form, the group that described the second compressor (200) selects free piston compressor, rotor-type compressor, screw compressor, centrifugal compressor to form.
20. compressor assembly as described as any one in claim 1-11, the compressor that wherein said the first compressor (100) and described the second compressor (200) they are same type.
21. compressor assembly as described as any one in claim 1-11, wherein said the first compressor (100) and described the second compressor (200) are dissimilar compressor.
22. compressor assembly as described as any one in claim 1-11, first section be connected with described the first compressor (100) of wherein said admission line (410) is configured to the fluid resistance that provides less than second section be connected with described the second compressor (200) of described admission line (410).
23. compressor assembly as claimed in claim 22, wherein at least one item in the quantity of the angle of the length by selecting described the first section and described the second section, cross-section area, bending, bending makes the fluid resistance of described the first section be less than the fluid resistance of described the second section.
24. compressor assembly as described as any one in claim 1-11, further comprise the 3rd compressor (300), the 3rd suction port (318) of described the 3rd compressor (300) is communicated with first suction port (118) of described the first compressor (100) and the second suction port (218) fluid of described the second compressor (200) respectively via described admission line (410), the 3rd relief opening (319) of described the 3rd compressor (300) is communicated with the first row gas port (119) of described the first compressor (100) and second row gas port (219) fluid of described the second compressor (200) respectively via described exhaust duct (420), and described the 3rd compressor (300) is communicated with described the first compressor (100) and described the second compressor (200) fluid via described oiling agent equalizing main (500).
25. compressor assembly as claimed in claim 24, be provided with gas equalizing main (600) between wherein said the second compressor (200) and described the 3rd compressor (300).
26. compressor assembly as claimed in claim 5 wherein is provided with throttle element in described oiling agent service (700).
27. compressor assembly as claimed in claim 26, wherein said throttle element is capillary tube.
28. compressor assembly as described as any one in claim 1-11, wherein said the first compressor (100) is configured with than the lower pressure of inspiration(Pi) of described the second compressor (200).
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320153166 CN203362462U (en) | 2013-03-29 | 2013-03-29 | Compressor system |
| PCT/CN2014/070991 WO2014154046A1 (en) | 2013-03-29 | 2014-01-21 | Compressor system and control method therefor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320153166 CN203362462U (en) | 2013-03-29 | 2013-03-29 | Compressor system |
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| Publication Number | Publication Date |
|---|---|
| CN203362462U true CN203362462U (en) | 2013-12-25 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201320153166 Expired - Lifetime CN203362462U (en) | 2013-03-29 | 2013-03-29 | Compressor system |
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| CN (1) | CN203362462U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104074726A (en) * | 2013-03-29 | 2014-10-01 | 艾默生环境优化技术(苏州)有限公司 | Compressor system and control method thereof |
| WO2014154046A1 (en) * | 2013-03-29 | 2014-10-02 | 艾默生环境优化技术(苏州)有限公司 | Compressor system and control method therefor |
| CN109139421A (en) * | 2018-08-24 | 2019-01-04 | 杰瑞石油天然气工程有限公司 | A kind of compaction control system of shared air cooler |
| WO2021179543A1 (en) * | 2020-03-09 | 2021-09-16 | 艾默生环境优化技术(苏州)有限公司 | Compressor system and oil management method for the compressor system |
-
2013
- 2013-03-29 CN CN 201320153166 patent/CN203362462U/en not_active Expired - Lifetime
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104074726A (en) * | 2013-03-29 | 2014-10-01 | 艾默生环境优化技术(苏州)有限公司 | Compressor system and control method thereof |
| WO2014154046A1 (en) * | 2013-03-29 | 2014-10-02 | 艾默生环境优化技术(苏州)有限公司 | Compressor system and control method therefor |
| CN104074726B (en) * | 2013-03-29 | 2016-08-17 | 艾默生环境优化技术(苏州)有限公司 | Compressor system and control method thereof |
| CN109139421A (en) * | 2018-08-24 | 2019-01-04 | 杰瑞石油天然气工程有限公司 | A kind of compaction control system of shared air cooler |
| WO2021179543A1 (en) * | 2020-03-09 | 2021-09-16 | 艾默生环境优化技术(苏州)有限公司 | Compressor system and oil management method for the compressor system |
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Granted publication date: 20131225 |