CN102748298A - Rotary compressor inspiration structure - Google Patents
Rotary compressor inspiration structure Download PDFInfo
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- CN102748298A CN102748298A CN2012101954338A CN201210195433A CN102748298A CN 102748298 A CN102748298 A CN 102748298A CN 2012101954338 A CN2012101954338 A CN 2012101954338A CN 201210195433 A CN201210195433 A CN 201210195433A CN 102748298 A CN102748298 A CN 102748298A
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Abstract
The invention discloses a rotary compressor inspiration structure. The structure comprises a motor, a compressor body, and an inspiration tube assembly connected to the compressor body, wherein the minimum diameter of air inlets corresponding with the inspiration tube assembly and in the compressor body is d, the apparent work volume of the rotary compressor is set as V, the refrigerating capacity of a unit mass refrigerant in the rotary compressor is set as q, the rotation speed of the motor is n, and the specific volume of the refrigerant under a Chinese standard test condition is v; and for any refrigerant, the minimum diameter of the air inlets in the compressor body under Chinese standards satisfies a case that units of d, V, q, n and v are mm, cm<3>, J/kg, r/min and m<3>/kg respectively.
Description
[technical field]
The present invention relates to Compressor Technology, relate in particular to a kind of rotary compressor air suction structure.
[background technique]
At present; Rotary compressor generally is divided into single cylinder rotary compressor and twin-tub rotation-type compressor; The selection of both inlet hole caliber sizes; Often just rule of thumb calculate, lack the foundation that inlet hole caliber size designed quantitative, can not effectively control the flow in the working procedure, volumetric efficiency, noise etc. according to Design Theory according to theory; Particularly twin-tub rotation-type compressor is divided into two kinds in single suction gas and double suction gas again, and the design of its inlet hole caliber is more complicated.As depicted in figs. 1 and 2, mostly the air-breathing groove on the intercommunicating pore on the upper cylinder of twin-tub rotation-type compressor air suction structure, the intercommunicating pore on the dividing plate, the lower cylinder is inclined hole, and mostly the air intake passage on the upper cylinder is two-part or one-part form.But the present rotatable frequency-changeable compressor of single suction cyclone has the poor inspiration phenomenon usually when high frequency, thereby the not enough phenomenon of refrigerating capacity when causing the compressor high frequency has also reduced the volumetric efficiency of compressor, influences compressor performance.
The patent No. is ZL200810027311.1, and patent name is in the patent of " air suction structure of twin-tub rotation-type compressor ", discloses a kind of depressed structure of single suction of rotary compressor; The depressed structure of this single suction comprises upper and lower cylinder and is arranged on the dividing plate between the upper and lower cylinder; On upper cylinder, offer air intake passage, this air intake passage radially connects cylinder wall, offers vent on the dividing plate; Also offer intercommunicating pore on the upper cylinder; This intercommunicating pore is communicated with air suction way with vent, offer air-breathing groove on the lower cylinder, and then lower cylinder inside is communicated with said vent.Wherein, mostly the air-breathing groove on the intercommunicating pore that upper cylinder is offered, the intercommunicating pore on the dividing plate, the lower cylinder is inclined hole, and the air intake passage on the upper cylinder is two-part or one-part form.
Single suction air compressor cost, the good manufacturability low of the patented product than the double suction air compressor, but lower cylinder poor inspiration phenomenon can appear in existing single suction cyclone rotatable compressor usually.Particularly frequency-changeable compressor is when high frequency, and this phenomenon is more obvious, and the not enough phenomenon of refrigerating capacity in the time of can causing the compressor high frequency has also reduced the volumetric efficiency of compressor, influences compressor performance.
[summary of the invention]
The present invention passes through the size of the restriction first cylinder intakeport, reasonably confirms the upper and lower suction port ratio of cylinder, oblique intakeport angle and upper and lower suction port and inlet hole ratio according to test, further limits the mathematical relationship of inlet hole and discharge capacity; Provide a kind of and can effectively improve compressor performance, air-breathing abundance, the refrigerating capacity of compressor (or heating capacity), COP, noise, vibration can have bigger improved rotary compressor air suction structure.
In order to realize the foregoing invention purpose, the technological scheme that the present invention adopts is:
A kind of rotary compressor air suction structure; Comprise motor, compressor body and be connected to the suction conduit assembly of said compressor body; The inlet hole minimum diameter of corresponding suction conduit assembly is that (d is actual in managing in the liquor separator before the single cylinder cylinder working chamber or before the shunting of single suction gas twin-tub cylinder, minimum internal diameter in the whole air intake passage for d in the compressor body; Or twin-tub double suction gas, d manages before two cylinder working chambers internal diameter sum of two minimums in the whole air intake passage in the liquor separator), the nominal swept volume of rotary compressor is set at V (cm
3), the refrigerating capacity of rotary compressor unit mass refrigeration agent is set at q (J/kg), and motor speed is n (r/min), and the refrigerant specific volume is v (m under the NBS test operating mode
3/ kg);
The theoretical air displacement V of per second then
AlwaysFor: V
Always=nV/60 (cm
3/ s);
Corresponding mass flow rate is:
Then the refrigerating capacity Q of per second is in theory:
The inlet hole minimum diameter of corresponding suction conduit assembly is d (mm) in the compressor body, then area S=π d
2/ 4 (mm
2); Under NBS, for any refrigerant, then the relation of V and S should satisfy:
That is:
Wherein the unit of d, V, q, n, v is respectively mm, cm
3, J/kg, r/min, m
3/ kg.
Preferably, said suction conduit assembly comprises sucking pipe and connected liquor separator; Said compressor body comprises bent axle, upper flange, lower flange, first cylinder, second cylinder and is arranged on the dividing plate between first, second cylinder; Said crankshaft installed is on said motor; It is terminal that said lower flange is arranged on said bent axle, and said upper flange is installed on the bent axle of said motor lower end; Said first cylinder is upper cylinder or lower cylinder, and the second corresponding cylinder is lower cylinder or upper cylinder, and said upper cylinder cooperates with said bent axle and is arranged between upper flange and the dividing plate, and said lower cylinder cooperates with said bent axle and is arranged between lower flange and the dividing plate; Offer air intake passage on first cylinder, this air intake passage radially connects the entire cylinder wall, and air intake passage is connected with the sucking pipe of said suction conduit assembly is terminal; Offer the dividing plate vent on the dividing plate, also offer first intercommunicating pore on first cylinder, first intercommunicating pore is communicated with air intake passage with the dividing plate vent, offers air-breathing groove on second cylinder, and then second cylinder interior is communicated with said dividing plate vent; Among said first intercommunicating pore, dividing plate vent and the air-breathing groove three all or part of, three apertures in all or part of, any two apertures in any aperture all or part of all with the angled angle [alpha] that is equal to of cylinder end face, the angle [alpha] span is more than or equal to 35 ° and smaller or equal to 65 °.
Preferably, the air-breathing groove of offering on said second cylinder is the skewed slot of second cylinder inner wall and end face of cutting sth. askew.
Preferably, said first cylinder suction port minimum diameter d1 that directly is communicated with compression chamber should satisfy with the choosing of air-breathing groove minimum diameter d2 that second cylinder directly is communicated with compression chamber:
Preferably, said liquor separator diameter of inner pipe is d3, and first, second cylinder suction port and air-breathing groove minimum diameter are respectively d1 and d2, pipe cross-section area in the liquor separator
The first cylinder suction port cross-section area
The second cylinder suction port cross-section area
The relation of pipe cross-section area S and first, second cylinder suction port cross-section area S1, S2 should satisfy in the said liquor separator: S
1+ S
2≤S.
Preferably, said liquor separator diameter of bore, sucking pipe diameter of bore divide the aperture that is clipped to first, second cylinder interior successively, and the air-flow path aperture of moving towards along gas reduces successively gradually; Said sucking pipe adopts one-part form to play the caliber of metering function or adopts the difference that plays metering function more than two sections and two sections to connect caliber, and the difference on the sucking pipe more than two sections and two sections connects caliber and also reduces gradually successively along the air-flow path aperture that gas moves towards.
Preferably; It is d5 and d4 that said sucking pipe adopts two sections different connecting tubes footpath diameters; The liquor separator diameter of bore of said liquor separator is d3; The suction port diameter that said first cylinder directly is communicated with compression chamber adopts two-part diameter d 6 and d7, and the diameter of air-breathing diameter at first cylinder, dividing plate and the second cylinder place that said second cylinder directly is communicated with compression chamber is respectively d8, d9 and d10, and the inlet hole minimum diameter of corresponding suction conduit assembly is d in the compressor body; From the liquor separator diameter of bore of liquor separator to the cylinder interior aperture; Aperture along two paths overdraught passages of gas trend should be followed successively by d3-d5-d4-d-d6-d7 and d3-d5-d4-d-d8-d9-d10, and the aperture on this two paths meets following relation: d3 >=d5 >=d4 >=d >=d6 >=d7; D3 >=d5 >=d4 >=d >=d8 >=d9 >=d10.The cross-section area of air intake passage should reduce gradually, can reduce the air intake passage gas-flow resistance like this, improves the flow velocity of air-flow, for cylinder provides sufficient more gas.In air intake passage the front or in the middle of a certain section or a few sections very cross-section area hour can cause compressor air suction not enough to air-breathing generation throttling phenomenon, refrigerating capacity descends, and also can cause the compressor gas noise to rise.
A kind of rotary compressor air suction structure comprises motor, compressor body and is connected to the suction conduit assembly of said compressor body that the inlet hole minimum diameter of corresponding suction conduit assembly is d in the compressor body, and the nominal swept volume of rotary compressor is set at V (cm
3), the refrigerating capacity of rotary compressor unit mass refrigeration agent is set at q (J/kg), and motor speed is n (r/min), and the refrigerant specific volume is v under the NBS test operating mode; The theoretical air displacement V of per second then
AlwaysFor: V
Always=nV/60 (cm
3/ s); Corresponding mass flow rate is:
Then the refrigerating capacity Q of per second is in theory:
The inlet hole minimum diameter of corresponding suction conduit assembly is d (mm) in the compressor body, then area S=π d
2/ 4 (mm
2); Under NBS, for any refrigerant, then the relation of V and S should satisfy:
That is:
Wherein the unit of d, V, q, n, v is respectively mm, cm
3, J/kg, r/min, m
3/ kg; Said suction conduit assembly comprises sucking pipe and connected liquor separator; Said compressor body comprises bent axle, upper flange, lower flange, first cylinder, second cylinder and is arranged on the dividing plate between first, second cylinder; Said crankshaft installed is on said motor; It is terminal that said lower flange is arranged on said bent axle, and said upper flange is installed on the bent axle of said motor lower end; Said first cylinder is a upper cylinder, and the second corresponding cylinder is a lower cylinder, and said upper cylinder cooperates with said bent axle and is arranged between upper flange and the dividing plate, and said lower cylinder cooperates with said bent axle and is arranged between lower flange and the dividing plate; Offer air intake passage on the dividing plate, this air intake passage radially outer edge direction connects partition wall, and air intake passage is connected with the sucking pipe of said suction conduit assembly is terminal, also offers the upper and lower vent that is communicated with respectively with air intake passage on the dividing plate; Offer the first air-breathing groove on first cylinder, the upper vent hole on the said dividing plate is communicated with air intake passage with the first air-breathing groove; Offer the second air-breathing groove on second cylinder, the following vent on the said dividing plate is communicated with air intake passage with the second air-breathing groove; Said upper vent hole, down among vent, the first air-breathing groove and the second air-breathing groove all or part of, four apertures in all or part of, any two apertures in any aperture all or part of all with the angled angle [alpha] that is equal to of cylinder end face, the angle [alpha] span is more than or equal to 35 ° and smaller or equal to 65 °.
Preferably, the first air-breathing groove of offering on said first cylinder is the skewed slot of the firstth cylinder inner wall and end face of cutting sth. askew, and the second air-breathing groove of offering on said second cylinder is the skewed slot of second cylinder inner wall and end face of cutting sth. askew.
Preferably, said first cylinder suction port minimum diameter d1 that directly is communicated with compression chamber should satisfy with the choosing of air-breathing groove minimum diameter d2 that second cylinder directly is communicated with compression chamber:
Preferably, said liquor separator diameter of inner pipe is d3, and the air-breathing groove minimum diameter of first, second cylinder is respectively d1 and d2, pipe cross-section area in the liquor separator
The first cylinder suction port cross-section area
The second cylinder suction port cross-section area
The relation of pipe cross-section area S and first, second cylinder suction port cross-section area S1, S2 should satisfy in the said liquor separator: S
1+ S
2≤S.
Preferably, said liquor separator diameter of bore, sucking pipe diameter of bore divide the air-breathing groove that is clipped to first, second cylinder interior footpath successively, and the air-flow path aperture of moving towards along gas reduces successively gradually; Said sucking pipe adopts one-part form to play the caliber of metering function or adopts the difference that plays metering function more than two sections and two sections to connect caliber, and the difference on the sucking pipe more than two sections and two sections connects caliber and also reduces gradually successively along the air-flow path aperture that gas moves towards.
Preferably; It is d5 and d4 that said sucking pipe adopts two sections different connecting tubes footpath diameters; The liquor separator diameter of bore of said liquor separator is d3; The diameter of air-breathing diameter at dividing plate, the first cylinder place that said first cylinder directly is communicated with compression chamber is respectively d11 and d12, and the diameter of air-breathing diameter at dividing plate, the second cylinder place that said second cylinder directly is communicated with compression chamber is respectively d13 and d14, and the inlet hole minimum diameter of corresponding suction conduit assembly is d in the compressor body; From the liquor separator diameter of bore of liquor separator to the cylinder interior aperture; Aperture along two paths overdraught passages of gas trend should be followed successively by d3-d5-d4-d-d11-d12 and d3-d5-d4-d-d13-d14, and the aperture on this two paths meets following relation: d3 >=d5 >=d4 >=d >=d11 >=d12; D3 >=d5 >=d4 >=d >=d13 >=d14.The cross-section area of air intake passage should reduce gradually, can reduce the air intake passage gas-flow resistance like this, improves the flow velocity of air-flow, for cylinder provides sufficient more gas.In air intake passage the front or in the middle of a certain section or a few sections very cross-section area hour can cause compressor air suction not enough to air-breathing generation throttling phenomenon, refrigerating capacity descends, and also can cause the compressor gas noise to rise.
The invention has the beneficial effects as follows:
The present invention chooses the upper and lower suction port of cylinder size according to test data, and the angle of inclination of the air-breathing groove of the intercommunicating pore offered of upper cylinder, the intercommunicating pore on the dividing plate, lower cylinder; Further confirm the proportionate relationship of upper and lower suction port size and inlet hole; And the relation of air intake passage size and discharge capacity, can reduce inhalation resistance, gettering efficiency; Improve compressor refrigerating capacity (or heating capacity), improve noise, the vibration of compressor Energy Efficiency Ratio, reduction compressor; Solved existing twin-tub or the air-breathing caliber of single cylinder compressor separatory and discharge capacity and selected, solved cylinder poor inspiration of twin-tub single suction air compressor and cause the not high problem of air compressor performance, and then reached and reduce air-breathing pulsation and vibration of compressor, noise.
In addition, the great majority that present single suction air compressor is communicated with liquor separator are upper cylinder, and the present invention can adopt lower cylinder to be communicated with liquor separator, can reduce the height of liquor separator with respect to complete machine, help compressor compact.Simultaneously, the first cylinder air intake passage adopts the effect of 3 stops also more obvious.
[description of drawings]
Fig. 1 is a kind of structural representation that first cylinder does not have current limliting in the existing twin-tub single suction air compressor;
Fig. 2 is another structural representation that first cylinder does not have current limliting in the existing twin-tub single suction air compressor;
Fig. 3 is that first cylinder is the structural representation of upper cylinder in the twin-tub single suction air compressor of the present invention;
Fig. 4 is that first cylinder is the structural representation of lower cylinder in the twin-tub single suction air compressor of the present invention;
Fig. 5 is the structural representation of corresponding first cylinder air-flow path when sucking pipe adopts the multi-section type current limliting in the twin-tub single suction air compressor of the present invention;
Fig. 6 is that the first cylinder suction port minimum diameter is that d1 and another cylinder (second cylinder) suction port minimum diameter are the structural representation of d2 in the twin-tub single suction air compressor of the present invention;
Fig. 7 is the schematic representation of oblique intakeport angle structure one in the twin-tub single suction air compressor of the present invention;
Fig. 8 is the schematic representation of oblique intakeport angle structure two in the twin-tub single suction air compressor of the present invention;
Fig. 9 is the schematic representation of oblique intakeport angle structure three in the twin-tub single suction air compressor of the present invention;
Figure 10 is the schematic representation of oblique intakeport angle structure four in the twin-tub single suction air compressor of the present invention;
Figure 11 is the schematic representation of oblique intakeport angle structure five in the twin-tub single suction air compressor of the present invention;
Figure 12 is the schematic representation of oblique intakeport angle structure six in the twin-tub single suction air compressor of the present invention;
Figure 13 is that the liquor separator diameter of inner pipe is d3 in the twin-tub single suction air compressor of the present invention, and first, second cylinder suction port minimum diameter is respectively the structural representation of d1 and d2;
Figure 14 be in the twin-tub single suction air compressor of the present invention in the compressor body inlet hole minimum diameter of corresponding suction conduit assembly be the structural representation of d;
Figure 15 is the structural representation of the liquor separator diameter of bore of liquor separator in the twin-tub single suction air compressor of the present invention to each cylinder interior aperture diameter;
Figure 16 is that the single suction gas twin-tub frequency-changeable compressor frequency of the present invention's 23.2 discharge capacities improves the variation rule curve of double suction gas twin-tub frequency-changeable compressor refrigerating capacity difference under unit area unit time refrigerating capacity of relative 23.2 discharge capacities down gradually;
Figure 17 is that the single suction gas twin-tub frequency-changeable compressor frequency of the present invention's 42.8 discharge capacities improves the variation rule curve of double suction gas twin-tub frequency-changeable compressor refrigerating capacity difference under unit area unit time refrigerating capacity of relative 42.8 discharge capacities down gradually;
Figure 18 is that the air-breathing minimum diameter d2 that single suction gas twin-tub frequency-changeable compressor second cylinder (lower cylinder) under frequency 30Hz of the present invention's 42.8 discharge capacities directly is communicated with compression chamber changes the variation rule curve that compressor refrigerating capacity is improved with the ratio that first cylinder (upper cylinder) directly is communicated with the suction port minimum diameter d1 of compression chamber;
Figure 19 is that the air-breathing minimum diameter d2 that single suction gas twin-tub frequency-changeable compressor second cylinder (lower cylinder) under frequency 60Hz of the present invention's 42.8 discharge capacities directly is communicated with compression chamber changes the variation rule curve that compressor refrigerating capacity is improved with the ratio that first cylinder (upper cylinder) directly is communicated with the suction port minimum diameter d1 of compression chamber;
Figure 20 is that the air-breathing minimum diameter d2 that single suction gas twin-tub frequency-changeable compressor second cylinder (lower cylinder) under frequency 80Hz of the present invention's 42.8 discharge capacities directly is communicated with compression chamber changes the variation rule curve that compressor refrigerating capacity is improved with the ratio that first cylinder (upper cylinder) directly is communicated with the suction port minimum diameter d1 of compression chamber.
[embodiment]
Embodiment one
A kind of rotary compressor air suction structure; Shown in figure 14; Comprise motor 1, compressor body 2 and be connected to the suction conduit assembly 3 of said compressor body, the inlet hole minimum diameter of corresponding suction conduit assembly is d in the compressor body 2, and the nominal swept volume of rotary compressor is set at V (cm
3), the refrigerating capacity of rotary compressor unit mass refrigeration agent is set at q (J/kg), and motor speed is n (r/min), and the refrigerant specific volume is v under the NBS test operating mode; The theoretical air displacement V of per second then
AlwaysFor: V
Always=nV/60 (cm
3/ s); Corresponding mass flow rate is:
Then the refrigerating capacity Q of per second is in theory:
Inlet hole minimum diameter d (mm) in the compressor body (d is actual in before in liquor separator, managing the shunting of twin-tub cylinder, the internal diameter of minimum in the whole air intake passage), then the area S=π d of the inlet hole in the compressor body 2
2/ 4 (mm
2); Under NBS; When the refrigeration agent that rotary compressor is selected for use is R410A; In order to study the loss of compressor refrigerating capacity, be reference object with the sufficient double suction gas twin-tub frequency-changeable compressor of gettering quantity (having two sucking pipes to give the upper and lower air cylinders air feed respectively), compare test with single suction gas twin-tub frequency-changeable compressor with it as testing machine; Two sucking pipes are kept supplying respectively, lower cylinder is air-breathing because double suction gas twin-tub frequency-changeable compressor has, and in the certain frequency scope, it is air-breathing to satisfy cylinder; The refrigerating capacity difference of contrast single suction gas twin-tub frequency-changeable compressor can instruct single suction gas twin-tub frequency-changeable compressor because the refrigerating capacity loss that intakeport causes greatly inadequately has much under same frequency.
As shown in table 1, in this embodiment's the test, double suction gas twin-tub frequency-changeable compressor and single suction gas twin-tub frequency-changeable compressor all adopt 23.2 discharge capacities, progressively improve compressor frequency, and its refrigerating capacity can improve, and needed gettering quantity also will improve.With unit area unit time cold in the table 1 is transverse axis, is the longitudinal axis with refrigerating capacity difference in the table 1, obtains shown in Figure 16; Because the intakeport of single suction gas twin-tub frequency-changeable compressor is big inadequately; Along with the raising of compressor frequency, compare with double suction gas twin-tub frequency-changeable compressor (air-breathing abundance), can cause poor inspiration; Show the phenomenon that refrigerating capacity reduces; Especially unit area unit time refrigerating capacity can obviously be found out from Figure 16 greater than after 50, because poor inspiration causes single suction gas twin-tub frequency-changeable compressor refrigerating capacity to decline to a great extent.
Equally, as shown in table 2, in another test of this embodiment, double suction gas twin-tub frequency-changeable compressor and single suction gas twin-tub frequency-changeable compressor all adopt 42.8 discharge capacities, progressively improve compressor frequency, and its refrigerating capacity can improve, and needed gettering quantity also will improve.With unit area unit time cold in the table 2 is transverse axis, is the longitudinal axis with refrigerating capacity difference in the table 2, obtains shown in Figure 17; Because the intakeport of single suction gas twin-tub frequency-changeable compressor is big inadequately; Along with the raising of compressor frequency, compare with double suction gas twin-tub frequency-changeable compressor (air-breathing abundance), also can cause poor inspiration; Show the phenomenon that refrigerating capacity reduces; Especially unit area unit time refrigerating capacity can obviously be found out from Figure 17 greater than after 50, because poor inspiration also causes single suction gas twin-tub frequency-changeable compressor refrigerating capacity to decline to a great extent.
Table 1
Table 2
In the test of table 1 and table 2, single suction gas duplex cylinder compressor and double suction gas duplex cylinder compressor are except that suction mechanism is different, and all the other are all identical; In table 1 and the table 2, the refrigerating capacity difference is meant that the refrigerating capacity of single suction gas duplex cylinder compressor deducts the refrigerating capacity institute value of double suction gas duplex cylinder compressor; Unit area unit time refrigerating capacity (being the Q/S in the formula) is divided by intakeport area gained (the intakeport area of single suction gas duplex cylinder compressor is meant the area of single intakeport, and the intakeport area of double suction gas duplex cylinder compressor is meant the area sum of two intakepories) by refrigerating capacity; The area at the minimum place of the internal diameter of (in liquor separator, managing cylinder compression chamber suction port) in the air intake passage that the intakeport area is meant; For twin-tub single suction air compressor, then refer in liquor separator, manage the minimum area of the preceding internal diameter of air intake passage shunting.
So, in order to guarantee compressor at work, sufficient gettering quantity is arranged, then the relation of V and S should satisfy
So the inlet hole minimum diameter in the compressor body 2 satisfies
Wherein the unit of d, V, q, n, v is respectively mm, cm
3, J/kg, r/min, m
3/ kg.
Above Test Example; Just through single suction gas twin-tub frequency-changeable compressor and double suction gas twin-tub frequency-changeable compressor comparison test; Explain that compressor unit area unit time refrigerating capacity is greater than after 50; Because poor inspiration also causes compressor refrigerating capacity to decline to a great extent; So in order to guarantee compressor at work, sufficient gettering quantity is arranged, chooses the interior inlet hole minimum diameter of compressor body satisfied
in the present embodiment; Compressor body both can be that the single cylinder rotary compressor can be a duplex-cylinder rotary compressor also, was not limited to the explanation in the above Test Example; Extremely shown in Figure 15 like Fig. 3; When compressor body is duplex-cylinder rotary compressor; Inlet hole in the compressor body both can be arranged on upper cylinder or the lower cylinder; Also can be arranged on the dividing plate between the upper and lower cylinder, corresponding inlet hole diameter all satisfies
(when the refrigeration agent of under NBS, selecting for use all is R410A).In addition; In the present embodiment; When the refrigeration agent that rotary compressor is selected for use is R410A; The relation of V and S should satisfy
when selecting other refrigeration agents for use; During like R22, R134a, R142b, R404A, R407C, R507; The corresponding relation of V and S satisfies
equally can be when adopting refrigeration agent R410A the test method checking, verify no longer one by one at this and to give unnecessary details.
Embodiment two
Like Fig. 3 to Figure 11, Figure 13 to shown in Figure 14; On embodiment one basis; Except satisfying inlet hole minimum diameter
; In this embodiment; Compressor body 2 is a duplex-cylinder rotary compressor, and suction conduit assembly 3 comprises sucking pipe 30 and connected liquor separator 31; Compressor body 2 comprises bent axle 20, upper flange 21, lower flange 22, first cylinder 23, second cylinder 24 and is arranged on the dividing plate 25 between first, second cylinder; Bent axle 20 is installed on the motor 1; Lower flange 22 is arranged on bent axle 20 ends, and upper flange 21 is installed on the bent axle 20 of motor 1 lower end; When first cylinder 23 was upper cylinder, the second corresponding cylinder 24 was a lower cylinder; When first cylinder 23 was lower cylinder, the second corresponding cylinder 24 was a upper cylinder; Upper cylinder cooperates with bent axle 20 and is arranged between upper flange 21 and the dividing plate 25, and lower cylinder cooperates with bent axle 20 and is arranged between lower flange 21 and the dividing plate 25.In this embodiment, offer air intake passage 4 on first cylinder 23, this air intake passage radially connects the entire cylinder wall and is communicated with cylinder working chamber, and air intake passage 4 is connected with sucking pipe 30 ends of suction conduit assembly 3; Offer dividing plate vent 250 on the dividing plate 25; Also offer first intercommunicating pore 230 on first cylinder 23; First intercommunicating pore 230 is communicated with air intake passage 4 with dividing plate vent 250; Offer the skewed slot of the air-breathing groove offered on air-breathing groove 240, the second cylinders 24 240 on second cylinder 24, and then second cylinder interior is communicated with dividing plate vent 250 for cut sth. askew second cylinder inner wall and end face; Among first intercommunicating pore 230, dividing plate vent 250 and air-breathing groove 240 threes all or part of, three apertures in all or part of, any two apertures in any aperture all or part of all with the angled angle [alpha] that is equal to of cylinder end face; As shown in Figure 7, the angled angle [alpha] that is equal to of whole and cylinder end face in three apertures among first intercommunicating pore 230, dividing plate vent 250 and air-breathing groove 240 threes; As shown in Figure 8; Among first intercommunicating pore 230, dividing plate vent 250 and air-breathing groove 240 threes; Have only the part aperture of dividing plate vent 250 and the whole apertures and the angled angle [alpha] that is equal to of cylinder end face of air-breathing groove 240, first intercommunicating pore 230 is offered perpendicular to air intake passage 4; As shown in Figure 9; Among first intercommunicating pore 230, dividing plate vent 250 and air-breathing groove 240 threes; Have only the part aperture and the angled angle [alpha] that is equal to of cylinder end face of dividing plate vent 250, first intercommunicating pore 230 is offered perpendicular to air intake passage 4, and air-breathing groove 240 tilts to offer; Shown in figure 10, among first intercommunicating pore 230, dividing plate vent 250 and air-breathing groove 240 threes, whole apertures of dividing plate vent 250 and air-breathing groove 240 all with the angled angle [alpha] that is equal to of cylinder end face, first intercommunicating pore 230 is offered perpendicular to air intake passage 4; Shown in figure 11, among first intercommunicating pore 230, dividing plate vent 250 and air-breathing groove 240 threes, the part aperture of first intercommunicating pore, 230 whole apertures, dividing plate vent 250, whole apertures of air-breathing groove 240 all with the angled angle [alpha] that is equal to of cylinder end face; Above structure just illustrates, and is not limited thereto in the practical implementation, and its angle [alpha] span is more than or equal to 35 ° and smaller or equal to 65 °; Adopt this angular range; Design from air suction structure has solved air-breathing bottleneck problem, and the air intake passage of gas flow obtains optimization, has shortened inspiratory circuit; Reduce inhalation resistance, improved gettering efficiency.
Embodiment three
Like Fig. 3 to Figure 11, Figure 13 to shown in Figure 14; The basis requires in satisfying embodiment two; In this embodiment; The air-breathing groove minimum diameter d2 that second cylinder 24 (lower cylinder) directly is communicated with compression chamber and first cylinder 23 (upper cylinder) directly are communicated with the ratio of the suction port minimum diameter d1 of compression chamber, and the refrigeration of compressor and the raising rate of heating capacity are had tangible influence.As shown in table 3, the single suction gas twin-tub frequency-changeable compressor that testing machine is chosen adopts 42.8 discharge capacities, and second cylinder 24 is a lower cylinder, and to choose the air-breathing minimum diameter d2 that second cylinder 24 directly is communicated with compression chambers be that 14mm is constant; First cylinder 23 is a upper cylinder, changes the suction port minimum diameter d1 size that first cylinder 23 directly is communicated with compression chamber, the raising that progressively improves compressor frequency, refrigerating capacity respectively, the test data contrast that records the different air-breathing schemes of 42.8 capacity compressors in the table 3; Get the variation rule curve of the variation of d2/d1 ratio to the compressor refrigerating capacity raising according to table 3; Shown in Figure 18 to 20; Abscissa representes that the air-breathing groove minimum diameter d2 that second cylinder directly is communicated with compression chamber and first cylinder directly are communicated with the ratio d2/d1 of the suction port minimum diameter d1 of compression chamber; Its scope is from 1 to 1.4, and y coordinate is represented the refrigerating capacity of compressor.Can know by Figure 18 to 20; The variation tendency of compressor refrigerating capacity is to be parabolical form, and when the air-breathing groove minimum diameter d2 that directly is communicated with compression chamber when second cylinder and first cylinder directly were communicated with the ratio d2/d1 from 1 to 1.2 of suction port minimum diameter d1 of compression chamber, the raising of compressor refrigerating capacity was parabola and rises; When ratio is 1.2 left and right sides; Reach the highest, from 1 to 1.4 o'clock, the raising of compressor refrigerating capacity was parabola and descends.Therefore; Poor inspiration when overcoming single suction air compressor high frequency; The phenomenon of scarce capacity; Improve compressor unit area unit time refrigerating capacity; The size of reasonable limits first cylinder 23 (upper cylinder) suction port when the aperture of first cylinder (upper cylinder) inlet hole is slightly less than the aperture of second cylinder (lower cylinder) inlet hole, can promote the ability of compressor; The air-breathing groove minimum diameter d2 that should keep second cylinder directly to be communicated with compression chamber is 1 to 1.2 with the ratio d2/d1 that first cylinder directly is communicated with the suction port minimum diameter d1 of compression chamber, and the air-breathing groove minimum diameter d2 that preferred second cylinder directly is communicated with compression chamber is 1.2 times of first cylinder suction port minimum diameter d1 that directly is communicated with compression chamber.In this case, could bonding air-breathing twin-tub frequency-changeable compressor when high frequency, have best service behaviour, air-breathing abundance improves the refrigeration performance of compressor greatly.
Table 3
Embodiment four
Like Fig. 3 to Figure 11, Figure 13 to shown in Figure 15; The basis required in satisfying embodiment three, in this embodiment, said liquor separator diameter of inner pipe was d3; First, second cylinder suction port and air-breathing groove minimum diameter are respectively d1 and d2, pipe cross-section area in the liquor separator
The first cylinder suction port cross-section area
The second cylinder suction port cross-section area
The relation of pipe cross-section area S and first, second cylinder suction port cross-section area S1, S2 should satisfy in the said liquor separator: S
1+ S
2≤S.The cross-section area of air intake passage should reduce gradually, can reduce the air intake passage gas-flow resistance like this, improves the flow velocity of air-flow, for cylinder provides sufficient more gas.In air intake passage the front or in the middle of a certain section or a few sections very cross-section area hour can cause compressor air suction not enough to air-breathing generation throttling phenomenon, refrigerating capacity descends, and also can cause the compressor gas noise to rise.
Embodiment five
Like Fig. 3 to Figure 11, Figure 13 to shown in Figure 15; The basis requires in satisfying embodiment four; In this embodiment, said liquor separator diameter of bore, sucking pipe diameter of bore divide the aperture that is clipped to first, second cylinder interior successively, and the air-flow path aperture of moving towards along gas reduces successively gradually; Sucking pipe adopts one-part form to play the caliber of metering function or adopts the difference that plays metering function more than two sections and two sections to connect caliber, and the difference on the sucking pipe more than two sections and two sections connects caliber and also reduces gradually successively along the air-flow path aperture that gas moves towards.As shown in Figure 5, on the sucking pipe more than two sections the difference of (d1---dm, dn) connect caliber and also reduce gradually successively along the air-flow path aperture of gas trend.Shown in figure 15; When sucking pipe adopts two sections different connecting tubes footpath diameters to be d5 and d4; The liquor separator diameter of bore of said liquor separator is d3; The suction port diameter that said first cylinder 23 directly is communicated with compression chamber adopts two-part diameter d 6 and d7, and the diameter of air-breathing diameter at first cylinder, dividing plate and the second cylinder place that said second cylinder 24 directly is communicated with compression chamber is respectively d8, d9 and d10, and the inlet hole minimum diameter of corresponding suction conduit assembly is d in the compressor body; From the liquor separator diameter of bore of liquor separator to the cylinder interior aperture; Aperture along two paths overdraught passages of gas trend should be followed successively by d3-d5-d4-d-d6-d7 and d3-d5-d4-d-d8-d9-d10; Aperture on this two paths meets following relation: d3 >=d5 >=d4 >=d >=d6 >=d7, d3 >=d5 >=d4 >=d >=d8 >=d9 >=d10.The cross-section area of air intake passage should reduce gradually, can reduce the air intake passage gas-flow resistance like this, improves the flow velocity of air-flow, for cylinder provides sufficient more gas.In air intake passage the front or in the middle of a certain section or a few sections very cross-section area hour can cause compressor air suction not enough to air-breathing generation throttling phenomenon, refrigerating capacity descends, and also can cause the compressor gas noise to rise.
Embodiment six
Like Figure 12 and shown in Figure 14; On embodiment one basis; Except satisfying inlet hole minimum diameter
; In this embodiment; Compressor body also is a duplex-cylinder rotary compressor, is to embodiment's five differences with embodiment two, and suction conduit assembly is installed on the dividing plate 25 between first, second cylinder (23,24).Wherein, suction conduit assembly comprises sucking pipe and connected liquor separator; Said compressor body comprises bent axle, upper flange, lower flange, first cylinder 23, second cylinder 24 and is arranged on the dividing plate 25 between first, second cylinder (23,24); Crankshaft installed is on motor; Lower flange is arranged on the bent axle end, and upper flange is installed on the bent axle of motor lower end; First cylinder 23 is a upper cylinder, and the second corresponding cylinder 24 is a lower cylinder, and upper cylinder cooperates with bent axle and is arranged between upper flange and the dividing plate 25, and lower cylinder cooperates with bent axle and is arranged between lower flange and the dividing plate 25; Offer air intake passage 4 on the dividing plate 25, this air intake passage radially outer edge direction connects partition wall, and air intake passage 4 is connected with the sucking pipe of suction conduit assembly is terminal, also offers the upper and lower vent (5,6) that is communicated with respectively with air intake passage on the dividing plate 25; Offer the first air-breathing groove 7 on first cylinder 23, the upper vent hole 5 on the dividing plate 25 is communicated with air intake passage 4 with the first air-breathing groove 7; Offer the second air-breathing groove 8 on second cylinder 24, the following vent 6 on the dividing plate 25 is communicated with air intake passage with the second air-breathing groove 8; The first air-breathing groove of offering on first cylinder 23 7 is the skewed slot of cut sth. askew first cylinder inner wall and end face, and the second air-breathing groove of offering on second cylinder 24 8 is the skewed slot of cut sth. askew second cylinder inner wall and end face.Said upper vent hole, down among vent, the first air-breathing groove and the second air-breathing groove all or part of, four apertures in all or part of, any two apertures in any aperture all or part of all with the angled angle [alpha] that is equal to of cylinder end face; The angle [alpha] span is more than or equal to 35 ° and smaller or equal to 65 °; Adopt this angular range; Design from air suction structure has solved air-breathing bottleneck problem, and the air intake passage of gas flow obtains optimization, has shortened inspiratory circuit; Reduce inhalation resistance, improved gettering efficiency.This embodiment and embodiment two are similar, in this explanation for example that differs.
Embodiment seven
The basis requires in satisfying embodiment six; In this embodiment; Like Figure 12 and shown in Figure 14; The air-breathing groove minimum diameter d1 that said first cylinder 23 directly is communicated with compression chamber should satisfy with the choosing of air-breathing groove minimum diameter d2 that second cylinder 24 directly is communicated with compression chamber: the mode of choosing and the embodiment three of d2/d1 ratio are similar among
this embodiment, in this explanation for example that differs.
Embodiment eight
The basis requires in satisfying embodiment seven, in this embodiment, like Figure 12 and shown in Figure 14; The liquor separator diameter of inner pipe is that d3 is (not shown in the figures; Can be with reference to the liquor separator assembly in other views), the air-breathing groove minimum diameter of first, second cylinder is respectively d1 and d2, pipe cross-section area in the liquor separator
The first cylinder suction port cross-section area
The second cylinder suction port cross-section area
The relation of pipe cross-section area S and first, second cylinder suction port cross-section area S1, S2 should satisfy in the said liquor separator: S
1+ S
2≤S, this embodiment and embodiment four are similar, in this explanation for example that differs.
Embodiment nine
The basis requires in satisfying embodiment eight; In this embodiment; Like Figure 12 and shown in Figure 14; Said liquor separator diameter of bore, sucking pipe diameter of bore divide the air-breathing groove that is clipped to first, second cylinder (23,24) inside footpath successively, and the air-flow path aperture of moving towards along gas reduces successively gradually; Said sucking pipe adopts one-part form to play the caliber of metering function or adopts the difference that plays metering function more than two sections and two sections to connect caliber, and the difference on the sucking pipe more than two sections and two sections connects caliber and also reduces gradually successively along the air-flow path aperture that gas moves towards.Shown in figure 14; When sucking pipe adopts two sections different connecting tubes footpath diameters is that d5 and d4 are (not shown in the figures; Can be with reference to sucking pipe aperture among Figure 15) time; The liquor separator diameter of bore of said liquor separator is d3; The diameter of air-breathing groove diameter at dividing plate 25, first cylinder, 23 places that first cylinder 23 directly is communicated with compression chamber is respectively d11 and d12, and the diameter of air-breathing groove diameter at dividing plate 25, second cylinder, 24 places that second cylinder 24 directly is communicated with compression chamber is respectively d13 and d14, and the inlet hole minimum diameter of corresponding suction conduit assembly 3 is d in the compressor body 2; From the liquor separator diameter of bore of liquor separator to the cylinder interior aperture; Aperture along two paths overdraught passages of gas trend should be followed successively by d3-d5-d4-d-d11-d12 and d3-d5-d4-d-d13-d14; Aperture on this two paths meets following relation: d3 >=d5 >=d4 >=d >=d11 >=d12, d3 >=d5 >=d4 >=d >=d13 >=d14.The cross-section area of air intake passage should reduce gradually, can reduce the air intake passage gas-flow resistance like this, improves the flow velocity of air-flow, for cylinder provides sufficient more gas.In air intake passage the front or in the middle of a certain section or a few sections very cross-section area hour can cause compressor air suction not enough to air-breathing generation throttling phenomenon, refrigerating capacity descends, and also can cause the compressor gas noise to rise.
The above embodiment for preferred embodiment of the present invention, is not to limit practical range of the present invention with this just, and the equivalence that all shapes according to the present invention, structure and principle are done changes, and all should be covered by in protection scope of the present invention.
Claims (13)
1. rotary compressor air suction structure; Comprise motor, compressor body and be connected to the suction conduit assembly of said compressor body; The inlet hole minimum diameter of corresponding suction conduit assembly is d in the compressor body, and the nominal swept volume of rotary compressor is set at V, and the refrigerating capacity of rotary compressor unit mass refrigeration agent is set at q; Motor speed is n, and the refrigerant specific volume is v under the NBS test operating mode; It is characterized in that:
Under NBS, for any refrigerant, the inlet hole minimum diameter in the said compressor body satisfies
Wherein the unit of d, V, q, n, v is respectively mm, cm
3, J/kg, r/min, m
3/ kg.
2. a kind of rotary compressor air suction structure according to claim 1 is characterized in that said suction conduit assembly comprises sucking pipe and connected liquor separator; Said compressor body comprises bent axle, upper flange, lower flange, first cylinder, second cylinder and is arranged on the dividing plate between first, second cylinder; Said crankshaft installed is on said motor; It is terminal that said lower flange is arranged on said bent axle, and said upper flange is installed on the bent axle of said motor lower end; Said first cylinder is upper cylinder or lower cylinder, and the second corresponding cylinder is lower cylinder or upper cylinder, and said upper cylinder cooperates with said bent axle and is arranged between upper flange and the dividing plate, and said lower cylinder cooperates with said bent axle and is arranged between lower flange and the dividing plate; Offer air intake passage on first cylinder, this air intake passage radially connects the entire cylinder wall, and air intake passage is connected with the sucking pipe of said suction conduit assembly is terminal; Offer the dividing plate vent on the dividing plate, also offer first intercommunicating pore on first cylinder, first intercommunicating pore is communicated with air intake passage with the dividing plate vent, offers air-breathing groove on second cylinder, and then second cylinder interior is communicated with said dividing plate vent; Among said first intercommunicating pore, dividing plate vent and the air-breathing groove three all or part of, three apertures in all or part of, any two apertures in any aperture all or part of all with the angled angle [alpha] that is equal to of cylinder end face, the angle [alpha] span is more than or equal to 35 ° and smaller or equal to 65 °.
3. a kind of rotary compressor air suction structure according to claim 2 is characterized in that, the air-breathing groove of offering on said second cylinder is the skewed slot of second cylinder inner wall and end face of cutting sth. askew.
4. a kind of rotary compressor air suction structure according to claim 2; It is characterized in that the suction port minimum diameter d1 that said first cylinder directly is communicated with compression chamber should satisfy with the choosing of air-breathing groove minimum diameter d2 that second cylinder directly is communicated with compression chamber:
5. a kind of rotary compressor air suction structure according to claim 2 is characterized in that said liquor separator diameter of inner pipe is d3, and first, second cylinder suction port and air-breathing groove minimum diameter are respectively d1 and d2, pipe cross-section area in the liquor separator
The first cylinder suction port cross-section area
The second cylinder suction port cross-section area
The relation of pipe cross-section area S and first, second cylinder suction port cross-section area S1, S2 should satisfy in the said liquor separator: S
1+ S
2≤S.
6. a kind of rotary compressor air suction structure according to claim 2; It is characterized in that; Said liquor separator diameter of bore, sucking pipe diameter of bore divide the aperture that is clipped to first, second cylinder interior successively, and the air-flow path aperture of moving towards along gas reduces successively gradually; Said sucking pipe adopts one-part form to play the caliber of metering function or adopts the difference that plays metering function more than two sections and two sections to connect caliber, and the difference on the sucking pipe more than two sections and two sections connects caliber and also reduces gradually successively along the air-flow path aperture that gas moves towards.
7. according to claim 5 and 6 described a kind of rotary compressor air suction structures; It is characterized in that; It is d5 and d4 that said sucking pipe adopts two sections different connecting tubes footpath diameters; The liquor separator diameter of bore of said liquor separator is d3; The suction port diameter that said first cylinder directly is communicated with compression chamber adopts two-part diameter d 6 and d7, and the diameter of air-breathing diameter at first cylinder, dividing plate and the second cylinder place that said second cylinder directly is communicated with compression chamber is respectively d8, d9 and d10, and the inlet hole minimum diameter of corresponding suction conduit assembly is d in the compressor body; To the cylinder interior aperture, should be followed successively by d3-d5-d4-d-d6-d7 and d3-d5-d4-d-d8-d9-d10 along the aperture of two paths overdraught passages of gas trend from the liquor separator diameter of bore of liquor separator, the aperture on this two paths meets following relation:
d3≥d5≥d4≥d≥d6≥d7；
d3≥d5≥d4≥d≥d8≥d9≥d10。
8. a kind of rotary compressor air suction structure according to claim 1 is characterized in that said suction conduit assembly comprises sucking pipe and connected liquor separator; Said compressor body comprises bent axle, upper flange, lower flange, first cylinder, second cylinder and is arranged on the dividing plate between first, second cylinder; Said crankshaft installed is on said motor; It is terminal that said lower flange is arranged on said bent axle, and said upper flange is installed on the bent axle of said motor lower end; Said first cylinder is a upper cylinder, and the second corresponding cylinder is a lower cylinder, and said upper cylinder cooperates with said bent axle and is arranged between upper flange and the dividing plate, and said lower cylinder cooperates with said bent axle and is arranged between lower flange and the dividing plate; Offer air intake passage on the dividing plate, this air intake passage radially outer edge direction connects partition wall, and air intake passage is connected with the sucking pipe of said suction conduit assembly is terminal, also offers the upper and lower vent that is communicated with respectively with air intake passage on the dividing plate; Offer the first air-breathing groove on first cylinder, the upper vent hole on the said dividing plate is communicated with air intake passage with the first air-breathing groove; Offer the second air-breathing groove on second cylinder, the following vent on the said dividing plate is communicated with air intake passage with the second air-breathing groove; Said upper vent hole, down among vent, the first air-breathing groove and the second air-breathing groove all or part of, four apertures in all or part of, any two apertures in any aperture all or part of all with the angled angle [alpha] that is equal to of cylinder end face, the angle [alpha] span is more than or equal to 35 ° and smaller or equal to 65 °.
9. a kind of rotary compressor air suction structure according to claim 8; It is characterized in that; The first air-breathing groove of offering on said first cylinder is the skewed slot of the firstth cylinder inner wall and end face of cutting sth. askew, and the second air-breathing groove of offering on said second cylinder is the skewed slot of second cylinder inner wall and end face of cutting sth. askew.
10. a kind of rotary compressor air suction structure according to claim 8; It is characterized in that the suction port minimum diameter d1 that said first cylinder directly is communicated with compression chamber should satisfy with the choosing of air-breathing groove minimum diameter d2 that second cylinder directly is communicated with compression chamber:
11. a kind of rotary compressor air suction structure according to claim 8 is characterized in that said liquor separator diameter of inner pipe is d3, the air-breathing groove minimum diameter of first, second cylinder is respectively d1 and d2, pipe cross-section area in the liquor separator
The first cylinder suction port cross-section area
The second cylinder suction port cross-section area
The relation of pipe cross-section area S and first, second cylinder suction port cross-section area S1, S2 should satisfy in the said liquor separator: S
1+ S
2≤S.
12. a kind of rotary compressor air suction structure according to claim 8; It is characterized in that; Said liquor separator diameter of bore, sucking pipe diameter of bore divide the air-breathing groove that is clipped to first, second cylinder interior footpath successively, and the air-flow path aperture of moving towards along gas reduces successively gradually; Said sucking pipe adopts one-part form to play the caliber of metering function or adopts the difference that plays metering function more than two sections and two sections to connect caliber, and the difference on the sucking pipe more than two sections and two sections connects caliber and also reduces gradually successively along the air-flow path aperture that gas moves towards.
13. according to claim 11 and 12 described a kind of rotary compressor air suction structures; It is characterized in that; It is d5 and d4 that said sucking pipe adopts two sections different connecting tubes footpath diameters; The liquor separator diameter of bore of said liquor separator is d3; The diameter of air-breathing diameter at dividing plate, the first cylinder place that said first cylinder directly is communicated with compression chamber is respectively d11 and d12, and the diameter of air-breathing diameter at dividing plate, the second cylinder place that said second cylinder directly is communicated with compression chamber is respectively d13 and d14, and the inlet hole minimum diameter of corresponding suction conduit assembly is d in the compressor body; To the cylinder interior aperture, should be followed successively by d3-d5-d4-d-d11-d12 and d3-d5-d4-d-d13-d14 along the aperture of two paths overdraught passages of gas trend from the liquor separator diameter of bore of liquor separator, the aperture on this two paths meets following relation:
d3≥d5≥d4≥d≥d11≥d12；
d3≥d5≥d4≥d≥d13≥d14。
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| CN113757116A (en) * | 2021-10-19 | 2021-12-07 | 广东美芝制冷设备有限公司 | Cylinder assembly, compression device and rotary compressor |
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