CN109002619A - The simulation optimization method of air-conditioner with fixed frequency compressor piping vibration - Google Patents
The simulation optimization method of air-conditioner with fixed frequency compressor piping vibration Download PDFInfo
- Publication number
- CN109002619A CN109002619A CN201810827978.3A CN201810827978A CN109002619A CN 109002619 A CN109002619 A CN 109002619A CN 201810827978 A CN201810827978 A CN 201810827978A CN 109002619 A CN109002619 A CN 109002619A
- Authority
- CN
- China
- Prior art keywords
- frequency
- vibration
- compressor
- crest
- intake duct
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
- G06F30/23—Design optimisation, verification or simulation using finite element methods [FEM] or finite difference methods [FDM]
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Theoretical Computer Science (AREA)
- Computer Hardware Design (AREA)
- Evolutionary Computation (AREA)
- Geometry (AREA)
- General Engineering & Computer Science (AREA)
- General Physics & Mathematics (AREA)
- Compressor (AREA)
Abstract
The present invention relates to finite element simulation fields, the indefinite problem in existing compressor piping system optimization direction, it is proposed a kind of simulation optimization method of air-conditioner with fixed frequency compressor piping vibration, model analysis and harmonic responding analysis are carried out for finite element model, the corresponding crest frequency of peak stress in identified sign frequency response curve, judge whether the result of harmonic responding analysis meets piping harmonic responding analysis evaluation criterion, if met, the trial-production processing of compressor piping is carried out, otherwise choose and compressor working frequency the smallest crest frequency of difference absolute value and be denoted as crest frequency one, it chooses and the smallest intrinsic frequency of difference absolute value of crest frequency one and obtains the corresponding natural mode of vibration of the intrinsic frequency and be denoted as natural mode of vibration one, the direction of vibration at the maximum position of Oscillation Amplitude and the position in finite element model is determined according to natural mode of vibration one , adjust the quality at the position and/or adjust rigidity of the position on direction of vibration.The present invention is suitable for the optimization of compressor piping system.
Description
Technical field
The present invention relates to finite element simulation field, in particular to a kind of emulation of air-conditioner with fixed frequency compressor piping vibration is simultaneously
The method optimized for simulation result.
Background technique
In air conditioner, compressor is that " heart " is also driving source, and being piped is connect compressor and air conditioner heat exchange system
Direct component, thus be piped vibration it is relatively large.For the piping evaluation of vibration aspect of air-conditioner with fixed frequency, have very in industry
More evaluation means such as first pass through simulation evaluation piping options, then further evaluate piping options by experimental test.Wherein, it imitates
True evaluation be evaluated by piping options superiority and inferiority of the simulation means to conceptual phase, such as application No. is
201810494640.0 Chinese patent proposes a kind of method of tire of air-conditioner with fixed frequency compressor piping vibration, the party
It is only proposed inside method and compressor piping system is established including the limited of compressor casing, fluid reservoir, air intake duct and exhaust pipe
Meta-model simultaneously evaluates whether piping can manufacture experimently processing after emulating to it according to the result of emulation, does not provide when emulating
It is piped how this optimizes when as a result not meeting evaluation criterion；And surveying test evaluation is by being piped in acquisition model machine
The data such as amplitude, stress so that piping options superiority and inferiority is evaluated.And at this stage, still whether by simulation means
Experience Design, the optimization to piping options are all that there are no a specific directions based on trial-and-error method.
Summary of the invention
The technical problems to be solved by the present invention are: overcoming existing compressor piping system optimization direction is indefinite to ask
Topic proposes a kind of simulation optimization method of air-conditioner with fixed frequency compressor piping vibration.
The present invention solves above-mentioned technical problem, the technical solution adopted is that:
The simulation optimization method of air-conditioner with fixed frequency compressor piping vibration, comprising the following steps:
A. the finite element model for determining compressor piping system and the observation point on finite element model；
B. is applied by boundary condition and carries out model analysis to it for finite element model and obtain the intrinsic frequency of finite element model
With corresponding natural mode of vibration, boundary condition is applied to finite element model and load motivates and carries out harmonic responding analysis to it and obtains
The stress frequency response curve of the observation point；
C. frequency corresponding to peak stress is denoted as crest frequency in identified sign frequency response curve, in judgment step b
Whether the result of harmonic responding analysis, which meets piping harmonic responding analysis evaluation criterion, carries out step d if meeting, otherwise, into step
Rapid e；
D. compressor piping carries out trial-production processing；
E. choose and compressor working frequency the smallest crest frequency of difference absolute value and the crest frequency is denoted as peak
It is worth frequency one, chooses and the smallest intrinsic frequency of difference absolute value of crest frequency one and to obtain the intrinsic frequency corresponding inherently
The vibration shape remembers that the natural mode of vibration is natural mode of vibration one, determines that Oscillation Amplitude is maximum in finite element model according to the natural mode of vibration one
Position and the position direction of vibration, which is denoted as position one；
F. the quality at position one is adjusted；And/or rigidity of the adjustment position one on the direction of vibration, enter step b.
Preferably, in the step f, if the crest frequency one is greater than the working frequency of compressor, reduce the portion
Quality at position one, and/or, increase rigidity of the position one on the direction of vibration；If the crest frequency one is less than compression
The working frequency of machine then increases the quality at the position one, and/or, reduce rigidity of the position one on the direction of vibration.
Further, in the step e, when the working frequency of compressor is greater than the minimum value of the crest frequency and is less than
When the maximum value of crest frequency, if the crest frequency one be greater than the working frequency, also choose be less than working frequency and with
The crest frequency is simultaneously denoted as crest frequency two by the smallest crest frequency of difference absolute value of working frequency, if crest frequency one is less than
The working frequency, then also choose be greater than working frequency and and working frequency the smallest crest frequency of difference and by the crest frequency
Be denoted as crest frequency two, in the presence of crest frequency two, also choose and crest frequency two the smallest intrinsic frequency of difference absolute value
And the corresponding natural mode of vibration of the intrinsic frequency is obtained, remember that the natural mode of vibration is natural mode of vibration two, according to the natural mode of vibration two
Determine the direction of vibration at the maximum position of Oscillation Amplitude and the position in finite element model, which is denoted as position two；
If the position two and the position one are inconsistent, step f further includes adjusting as follows: if the crest frequency two
Greater than the working frequency of compressor, then reduce the quality at the position two, and/or, increase position two in the direction of vibration
On rigidity；If the crest frequency two is less than compressor operating frequency, increase the quality at the position two, and/or, subtract
Few rigidity of the position two on the direction of vibration.
Preferably, in the step a, finite element model includes compressor casing, four-way valve, is connected with compressor casing
Fluid reservoir, fixing compressor cylinder body Rubber foot, be connected to fluid reservoir air entry and the air intake duct of four-way valve, be connected to compressor cylinder
The exhaust pipe of the exhaust outlet of body and four-way valve, the connecting tube one for connecting four-way valve and heat exchanger and for connect four-way valve with
The connecting tube two of shut-off valve, the connecting tube one include boundary nozzle one and boundary nozzle two, and the connecting tube two includes boundary
Nozzle three, compressor include compressor casing and fluid reservoir.
Preferably, the air intake duct includes from outwardly extending the first extension of air intake duct of air entry of fluid reservoir, connection
The first turn of bilge of air intake duct of the first extension of air intake duct end bend, from the end of first turn of bilge of air intake duct with parallel
The second extension of air intake duct and the connection air intake duct extended in the extending direction receipt of first extension of air intake duct the
The second turn of bilge of air intake duct of two extension end bends；
The exhaust pipe includes from described in outwardly extending the first extension of exhaust pipe of exhaust outlet of compressor casing, connection
The first turn of bilge of exhaust pipe of exhaust pipe the first extension end bend, from the end of first turn of bilge of exhaust pipe to be parallel to
The second extension of exhaust pipe and the connection exhaust pipe second for stating the extending direction receipt extension of the first extension of exhaust pipe prolong
The second turn of bilge of exhaust pipe of extending portion end bend；
The observation point include at least observation point one and observation point two, the observation point one be located at the first turn of bilge of air intake duct and
At the first extension of air intake duct, the observation point two is located at the first turn of bilge of exhaust pipe and close to the first extension of exhaust pipe.
Further, in step b, the boundary condition is the fixation staff cultivation and boundary nozzle one, side of rubber foot plate surface
The fixed constraint of boundary's nozzle two and boundary nozzle three, the Rubber foot are three.
Preferably, in step b, the load is actuated to two node unit displacement load, and two node is in compressor cylinder
It is symmetric that direction of displacement is opposite and carrier phase shift 180 degree on body.
Preferably, in step b, preceding 20 rank intrinsic frequency that the model analysis is piped and intrinsic with preceding 20 rank
The corresponding natural mode of vibration of frequency.
Preferably, in step b, the harmonic responding analysis method is complete method, and the starting of frequency is analyzed in the complete method
Value is that the working frequency of compressor subtracts 20Hz, analyzes the stop value of frequency as the working frequency of compressor and adds 20Hz.
Preferably, the piping harmonic responding analysis evaluation criterion are as follows: the working frequency of the crest frequency and compressor it
The least absolute value of difference is not less than 8Hz, and the work of frequency and compressor corresponding to 0.618 times of value of the amplitude of peak stress
The least absolute value of the difference of frequency is not less than 6Hz.
The beneficial effects of the present invention are:
1) change in a manner of the compressor piping Optimized System Design based on trial-and-error method, match for the compressor of air-conditioner with fixed frequency
Guard system optimization specifies specific direction, i.e. the quality at the adjustment position one in step g；And/or adjustment position one is in the vibration
Rigidity on dynamic direction, so that the natural frequency of vibration gap of the working frequency of compressor and compressor piping system is increased and then reduced
The vibration of compressor piping.
2) direction of piping options optimization has been further clarified, i.e. the quality at position one is to increase or reduce, position one
Rigidity on the direction of vibration is to increase or reduce.
3) when compressor operating frequency is greater than the minimum value of the crest frequency and is less than the minimum value of crest frequency, and
When position one and position two are inconsistent, further adjustment direction is specified, i.e., in the quality at adjustment position two or direction of vibration
Rigidity.
4) it quickly determines Piping design proposal, shortens the design cycle.
Detailed description of the invention
Fig. 1 is the air-conditioner with fixed frequency of the embodiment of the present invention with the flow chart of the simulation optimization method of tube vibration；
Fig. 2 is the structural schematic diagram of the finite element model of the embodiment of the present invention one；
Fig. 3 is the stress frequency response curve of observation point one in the former compressor piping system of the embodiment of the present invention one；
Fig. 4 is the stress frequency response curve of observation point two in the former compressor piping system of the embodiment of the present invention one；
Fig. 5 be the embodiment of the present invention one optimization after in compressor piping system observation point one stress frequency response curve
Figure；
Fig. 6 be the embodiment of the present invention one optimization after in compressor piping system observation point two stress frequency response curve
Figure；
Fig. 7 is the structural schematic diagram of the finite element model of the embodiment of the present invention two；
Fig. 8 is the stress frequency response curve of observation point one in the former compressor piping system of the embodiment of the present invention two；
Fig. 9 is the stress frequency response curve of observation point two in the former compressor piping system of the embodiment of the present invention two；
Figure 10 is bent for the stress frequency response of observation point one in compressor piping system after the optimization of the embodiment of the present invention two
Line chart；
Figure 11 is bent for the stress frequency response of observation point two in compressor piping system after the optimization of the embodiment of the present invention two
Line chart；
Wherein, 1 is compressor casing, and 2 be four-way valve, and 3 be fluid reservoir, and 4 be Rubber foot, and 5 be air intake duct, and 50 be air intake duct
First extension, 51 be the first turn of bilge of air intake duct, and 52 be the second extension of air intake duct, and 53 be the second turn of bilge of air intake duct, and 54 be sight
Measuring point one, 6 be exhaust pipe, and 60 be the first extension of exhaust pipe, and 61 be the first turn of bilge of exhaust pipe, and 62 extend for exhaust pipe second
Portion, 63 be the second turn of bilge of exhaust pipe, and 64 be observation point two, and 7 be connecting tube one, and 71 be boundary nozzle one, and 72 be boundary nozzle two,
8 be connecting tube two, and 81 be boundary nozzle three.
Specific embodiment
In order to make the objectives, technical solutions, and advantages of the present invention clearer, right with reference to the accompanying drawings and embodiments
The present invention is further elaborated.
The present invention is directed to overcome the problems, such as that existing compressor piping system optimization direction is indefinite, a kind of fixed frequency air conditioner is proposed
The simulation optimization method of device compressor piping vibration, as shown in Figure 1, method includes the following steps:
A. the finite element model for determining compressor piping system and the observation point on finite element model；
Using the air conditioner with refrigeration and heat-production functions as reference, so that finite element model and actual test have refrigerated medium
The air conditioner actual measurement response of heat function is consistent, preferably, finite element model may include compressor casing, four-way valve and compression
The connected fluid reservoir of machine cylinder body, fixing compressor cylinder body Rubber foot, be connected to the air entry of fluid reservoir and the air intake duct of four-way valve,
It is connected to the exhaust outlet of compressor casing and the exhaust pipe of four-way valve, the connecting tube one for connecting four-way valve and heat exchanger and is used for
The connecting tube two of four-way valve and shut-off valve is connected, connecting tube one includes boundary nozzle one and boundary nozzle two, and connecting tube two includes
Boundary nozzle three, compressor include compressor casing and fluid reservoir.
The larger position of stress is to concentrate on the first turn of bilge of the first turn of bilge of air intake duct and exhaust pipe when because matching tube vibration, this is at two
Stress frequency response data more can accurately reflect piping vibrational state, so observation point at least two and being located at suction
The first turn of bilge of the first turn of bilge of tracheae and exhaust pipe, certain observation point more mostly just more can accurately reflect the vibrational state of piping.It is preferred that
, air intake duct may include extending from outwardly extending the first extension of air intake duct of air entry, the connection air intake duct first of fluid reservoir
The first turn of bilge of air intake duct of portion's end bend, the first turn of bilge of self-priming tracheae end to be parallel to prolonging for the first extension of air intake duct
The air intake duct second of the second extension of air intake duct and connection the second extension of air intake duct end bend of stretching the extension of direction receipt is curved
Portion.Exhaust pipe may include outwardly extending the first extension of exhaust pipe of exhaust outlet, the connection exhaust pipe first from compressor casing
The first turn of bilge of exhaust pipe of extension end bend, from the end of the first turn of bilge of exhaust pipe to be parallel to the first extension of exhaust pipe
The second extension of exhaust pipe for extending of extending direction receipt and connect the exhaust pipe the of the second extension of exhaust pipe end bend
Two turn of bilges.Observation point includes at least observation point one and observation point two, and observation point one is located at the first turn of bilge of air intake duct and close to air-breathing
At the first extension of pipe, observation point two is located at the first turn of bilge of exhaust pipe and close to the first extension of exhaust pipe.
B. is applied by boundary condition and carries out model analysis to it for finite element model and obtain the intrinsic frequency of finite element model
With corresponding natural mode of vibration, boundary condition is applied to finite element model and load motivates and carries out harmonic responding analysis to it and obtains
The stress frequency response curve of observation point；
Boundary condition is the fixation staff cultivation and boundary nozzle one, boundary nozzle two and boundary nozzle three of rubber foot plate surface
Fixed constraint, Rubber foot are three.In order to cover intrinsic frequency corresponding to the crest frequency in harmonic responding analysis frequency band and
Natural mode of vibration, it is preferred that preceding 20 rank intrinsic frequency that model analysis can be piped and corresponding with preceding 20 rank intrinsic frequency
Natural mode of vibration.Load is actuated to two node unit displacement load, and two nodes are symmetric direction of displacement on compressor casing
Opposite and carrier phase shift 180 degree.In order to enable calculating speed and calculated result matching are optimal, it is preferred that harmonic responding analysis side
Method is complete method, and the initial value of analysis frequency is that the working frequency of compressor subtracts 20Hz in complete method, analyzes the termination of frequency
Value is that the working frequency of compressor adds 20Hz.
C. frequency corresponding to peak stress is denoted as crest frequency in identified sign frequency response curve, in judgment step b
Whether the result of harmonic responding analysis, which meets piping harmonic responding analysis evaluation criterion, carries out step d if meeting, otherwise, into step
Rapid e；
Matched by actual measurement and simulating, verifying when the absolute value of the difference of the working frequency of crest frequency and compressor is 6Hz
Tube vibration is preferable, along with therefore difference being limited to 8Hz to further guarantee that piping is once trial-produceed successfully.Stress peak
The least absolute value of the difference of the corresponding frequency of 0.618 times of value of the amplitude of value and the working frequency of compressor, which is set as 6Hz, is
In order to which the biggish Frequency point of proof stress concentrates near crest frequency point, without extending near compressor operating Frequency point
And then guarantee that probability is once trial-produceed in piping successfully.It is piped harmonic responding analysis evaluation criterion are as follows: the work of crest frequency and compressor
The least absolute value of the difference of frequency is not less than 8Hz, and frequency and compressor corresponding to 0.618 times of value of the amplitude of peak stress
Working frequency difference least absolute value be not less than 6Hz.
D. compressor piping carries out trial-production processing；
E. it chooses the smallest crest frequency of difference absolute value with the working frequency of compressor and is denoted as crest frequency one, selection
And the smallest intrinsic frequency of difference absolute value of crest frequency one simultaneously obtains the corresponding natural mode of vibration of the intrinsic frequency and is denoted as solid
There is the vibration shape one, the direction of vibration at the maximum position of Oscillation Amplitude and the position in finite element model determined according to natural mode of vibration one,
The position is denoted as position one；
Further, in order to which the solution of the present invention made is more perfect, in step e, when the working frequency of compressor is greater than
The minimum value of crest frequency and be less than crest frequency maximum value when, if crest frequency one be greater than working frequency, also choose small
In working frequency and and working frequency the smallest crest frequency of difference absolute value and the crest frequency is denoted as crest frequency two, if
Crest frequency one be less than working frequency, then also choose be greater than working frequency and and working frequency the smallest crest frequency of difference and will
The crest frequency is denoted as crest frequency two, in the presence of crest frequency two, also chooses and the difference absolute value of crest frequency two is minimum
Intrinsic frequency and obtain the corresponding natural mode of vibration of the intrinsic frequency, remember the natural mode of vibration be natural mode of vibration two, according to intrinsic
The vibration shape two determines the direction of vibration at the maximum position of Oscillation Amplitude and the position in finite element model, which is denoted as position two；
F. the quality at position one is adjusted；And/or rigidity of the adjustment position one on direction of vibration, enter step b.
To make the natural frequency of vibration gap increasing of the working frequency and compressor piping system of compressor reduce compressor in turn
The vibration of piping, it is preferred that in step f, if crest frequency one is greater than the working frequency of compressor, reduce the matter at position one
Amount, and/or, increase rigidity of the position one on direction of vibration；If crest frequency one is less than the working frequency of compressor, increase
Quality at position one, and/or, reduce rigidity of the position one on direction of vibration.
Further, in the presence of position two, if position two and position one are inconsistent, step f further includes adjusting as follows:
If crest frequency two is greater than the working frequency of compressor, reduce the quality at position two, and/or, increase position two and is vibrating
Rigidity on direction；If crest frequency two is less than compressor operating frequency, increase the quality at position two, and/or, reduction portion
Rigidity of the position two on direction of vibration.
The present invention is changed by step e and step f in a manner of the compressor piping Optimized System Design based on trial-and-error method, is
The compressor piping system optimization of air-conditioner with fixed frequency specifies specific direction, has further clarified the direction of piping options optimization,
The quality for vibrating maximum position is to increase or reduce and/or vibrate rigidity of the maximum position on the direction of vibration
It is to increase or reduce, and then quickly determine Piping design proposal, shortens the design cycle.
Embodiment one
As shown in Fig. 2, finite element model may include compressor casing 1, four-way valve 2, the liquid storage being connected with compressor casing 1
Tank 3, fixing compressor cylinder body 1 Rubber foot 4, connect fluid reservoir 3 air entry and the air intake duct 5 of four-way valve 2, connect compressor
The exhaust pipe 6 of the exhaust outlet of cylinder body 1 and four-way valve 2, for connecting four-way valve 2 with the connecting tube 1 of heat exchanger and for connecting
The connecting tube 28 of four-way valve 2 and shut-off valve, connecting tube 1 include boundary nozzle 1 and boundary nozzle 2 72, connecting tube 28
Including boundary nozzle 3 81.
Air intake duct 5 includes from outwardly extending the first extension of air intake duct 50 of air entry of fluid reservoir 3, connection air intake duct the
The first turn of bilge of air intake duct 51 of one extension, 50 end bend, the first turn of bilge of self-priming tracheae 51 end to be parallel to air intake duct
The second extension of air intake duct 52 and connection 52 end of the second extension of air intake duct that the extending direction receipt of one extension 50 extends
Curved the second turn of bilge of air intake duct 53, the second turn of bilge of air intake duct 53 is that space is curved in the present embodiment.
Exhaust pipe 6 includes being vented from outwardly extending the first extension of exhaust pipe 60 of exhaust outlet of compressor casing 1, connection
The first turn of bilge of exhaust pipe 61 of 60 end bend of the first extension of pipe is vented from the end of the first turn of bilge of exhaust pipe 61 with being parallel to
The second extension of exhaust pipe 62 and connection the second extension of exhaust pipe 62 that the extending direction receipt of the first extension of pipe 60 extends
The second turn of bilge of exhaust pipe 63 of end bend.
Observation point includes observation point 1 and observation point 2 64, and observation point 1 is located at the first turn of bilge of air intake duct 51 and close
The first extension of air intake duct 50, observation point 2 64 are located on the first turn of bilge of exhaust pipe 61 and close to the first extensions of exhaust pipe 60.
Model analysis is carried out after applying boundary condition to finite element model, wherein boundary condition is consolidating for 4 bottom surface of Rubber foot
Determine the fixed constraint of staff cultivation and boundary nozzle 1, boundary nozzle 2 72 and boundary nozzle 3 73, Rubber foot 4 is at least three
It is a；The preceding 20 rank intrinsic frequency and natural mode of vibration corresponding with preceding 20 rank intrinsic frequency that model analysis can be piped, inherently
List of frequency is as shown in table 1.
Table 1
Boundary condition and load excitation are applied to finite element model and harmonic responding analysis is carried out to obtain observation point to it
Stress frequency response curve.Wherein, boundary condition is consistent with above-mentioned boundary condition, and load is actuated to two modal displacements, two nodes
It is symmetric that direction of displacement is opposite and carrier phase shift 180 degree on compressor casing 1.Harmonic responding analysis method is using complete
Method, the initial value that frequency is analyzed in complete method is that the working frequency of compressor subtracts 20Hz, analyzes the stop value of frequency as compression
The working frequency of machine adds 20Hz, and the working frequency of fixed frequency air conditioner compressor is 50Hz in the present embodiment, so harmonic responding analysis frequency
The range of rate be 30Hz~70Hz, obtain observation point one as shown in Figure 3 stress frequency response curve and sight as shown in Figure 4
The stress frequency response curve of measuring point two.
Crest frequency point in the present embodiment in harmonic responding analysis result at observation point one and observation point two is almost the same, respectively
Crest frequency corresponding to peak stress is 40Hz, 48Hz, 68Hz, the least absolute value with the working frequency 50Hz of compressor
For 2Hz, do not meet in evaluation criterion " least absolute value of the difference of the working frequency of crest frequency and compressor is not less than
8Hz".Thus compressor piping can not carry out trial-production processing, need to enter following piping optimization specific steps.
In the present embodiment because observation point one and the crest frequency of observation point two are not much different, so be only with observation point one
Example carries out piping Optimization Work, otherwise needs to carry out for the crest frequency of observation point one and observation point two respectively corresponding excellent
Change.In the present embodiment and the smallest crest frequency one of the difference absolute value of the working frequency of compressor is 48Hz, because of the present embodiment
In compressor operating frequency 50Hz be greater than crest frequency minimum value 40Hz and be less than crest frequency maximum value 68Hz when, then
Also need to choose be greater than working frequency and and working frequency the smallest crest frequency 68Hz of difference absolute value as crest frequency two,
According to table 1 and the smallest intrinsic frequency of difference absolute value of one 48Hz of crest frequency be the 9th rank intrinsic frequency 47Hz, with peak
The smallest intrinsic frequency of difference absolute value for being worth two 68Hz of frequency is the intrinsic frequency 68.2Hz of the 12nd rank, according to the 9th intrinsic frequency of rank
The corresponding natural mode of vibration of rate 47HZ learns that Oscillation Amplitude maximum position i.e. position one is the bottom of the second turn of bilge of air intake duct 53, vibration
Direction is to be parallel to U-shaped 53 place in-plane of the second turn of bilge of air intake duct vibration, and Oscillation Amplitude is most in the 12nd rank natural mode of vibration
Big position and position two are the bottom of the second turn of bilge of exhaust pipe 63, and direction of vibration is along the space where the second turn of bilge of exhaust pipe 63
Turn around the tangential direction vibration of compressor casing.
Above-mentioned position one and position two are inconsistent, thus should carry out separating adjustment, crest frequency one in the present embodiment
48Hz is less than the working frequency 50Hz of compressor, should increase the quality at position one or reduce position one on corresponding direction of vibration
Rigidity, the present embodiment, which is taken, moves down 20mm for the second turn of bilge of air intake duct 53, not only increased the curved quality of air-breathing tube space in this way but also
Reduce the rigidity on its direction of vibration；And two 68Hz of crest frequency is greater than the working frequency of compressor in the present embodiment
50Hz；Quality at position two should also be reduced or increase rigidity of the position two on corresponding direction of vibration, taken exhaust pipe the
Two turn of bilges 63 move up 20mm, and become U-shaped curved for space is curved, have not only reduced the quality of the second turn of bilge of exhaust pipe in this way but also have increased
Rigidity on its direction of vibration.
Piping options after optimization are re-started into simulation analysis, compressor piping system after being optimized as shown in Figure 5
In observation point one stress frequency response curve and observation point two after optimization in compressor piping system is answered as shown in Figure 6
Power frequency response curve, crest frequency corresponding to each peak stress is 39Hz and 69Hz in harmonic responding analysis result, with pressure
The least absolute value of the working frequency 50Hz of contracting machine is the 8HZ that 11Hz is greater than in harmonic responding analysis evaluation criterion, peak stress
The corresponding frequency of 0.618 times of value of the amplitude of 39Hz and 69Hz is respectively the difference of the working frequency of 42Hz and 64Hz and compressor
Least absolute value be 8Hz be not less than 6Hz, therefore optimize after compressor piping can carry out trial-production processing.
Embodiment two
The present embodiment is with embodiment one the difference is that the stress frequency response curve of observation point one and observation point two
It is upper that there is only a peak stresses respectively.
As shown in fig. 7, finite element model may include compressor casing 1, four-way valve 2, the liquid storage being connected with compressor casing 1
Tank 3, fixing compressor cylinder body 1 Rubber foot 4, connect fluid reservoir 3 air entry and the air intake duct 5 of four-way valve 2, connect compressor
The exhaust pipe 6 of the exhaust outlet of cylinder body 1 and four-way valve 2, for connecting four-way valve 2 with the connecting tube 1 of heat exchanger and for connecting
The connecting tube 28 of four-way valve 2 and shut-off valve, connecting tube 1 include boundary nozzle 1 and boundary nozzle 2 72, connecting tube 28
Including boundary nozzle 3 81.
Air intake duct 5 includes from outwardly extending the first extension of air intake duct 50 of air entry of fluid reservoir 3, connection air intake duct the
The first turn of bilge of air intake duct 51 of one extension, 50 end bend, the first turn of bilge of self-priming tracheae 51 end to be parallel to air intake duct
The second extension of air intake duct 52 and connection 52 end of the second extension of air intake duct that the extending direction receipt of one extension 50 extends
Curved the second turn of bilge of air intake duct 53；Wherein, the second extension of air intake duct 52 is longer than the extension of the air intake duct second in embodiment one
Portion 52.
Exhaust pipe 6 includes being vented from outwardly extending the first extension of exhaust pipe 60 of exhaust outlet of compressor casing 1, connection
The first turn of bilge of exhaust pipe 61 of 60 end bend of the first extension of pipe is vented from the end of the first turn of bilge of exhaust pipe 61 with being parallel to
The second extension of exhaust pipe 62 and connection the second extension of exhaust pipe 62 that the extending direction receipt of the first extension of pipe 60 extends
The second turn of bilge of exhaust pipe 63 of end bend.
Observation point include at least observation point 1 and observation point 2 64, observation point 1 be located at the first turn of bilge of air intake duct 51 and
Close to the first extension of air intake duct 50, observation point 2 64 is located on the first turn of bilge of exhaust pipe 61 and close to the first extension of exhaust pipe
60。
Boundary condition is applied to finite element model and model analysis is carried out to it, wherein boundary condition is 4 bottom surface of Rubber foot
Fixation staff cultivation and boundary nozzle 1, boundary nozzle 2 72 and boundary nozzle 3 73 fixed constraint, Rubber foot 4 is at least
Three；The preceding 20 rank intrinsic frequency and natural mode of vibration corresponding with preceding 20 rank intrinsic frequency that model analysis can be piped, Gu
There is list of frequency as shown in table 2.
Table 2
Boundary condition and load excitation are applied to finite element model and harmonic responding analysis is carried out to obtain observation point to it
Stress frequency response curve.Wherein, boundary condition is consistent with above-mentioned boundary condition, and load is actuated to two modal displacements, two nodes
It is symmetric that direction of displacement is opposite and carrier phase shift 180 degree on compressor casing 1.Harmonic responding analysis method is complete
Method, the initial value that frequency is analyzed in complete method is that the working frequency of compressor subtracts 20Hz, analyzes the stop value of frequency as compression
The working frequency of machine adds 20Hz, and the working frequency of fixed frequency air conditioner compressor is 50Hz in the present embodiment, so harmonic responding analysis frequency
The range of rate be 30Hz~70Hz, obtain observation point one as shown in Figure 8 stress frequency response curve and sight as shown in Figure 9
The stress frequency response curve of measuring point two.
Only one peak stress of observation point one in harmonic responding analysis result, corresponding crest frequency are in the present embodiment
53Hz, also only one peak stress, corresponding crest frequency are 54Hz to observation point two, do not meet " crest frequency and compression
The least absolute value of the difference of the working frequency of machine is not less than the standard of 8Hz ", thus the trial-production that can not carry out compressor piping is pressed to add
Work needs to enter following piping optimization specific steps.
In the present embodiment because observation point one and the crest frequency of observation point two are not much different, so by taking observation point one as an example
Piping Optimization Work is carried out, otherwise needs to be optimized accordingly for the crest frequency of observation point one and observation point two respectively.
Specifically, and compressor working frequency the smallest crest frequency one of difference absolute value be 53Hz.According to table 2 frequently with peak value
The smallest intrinsic frequency of difference absolute value of one 53Hz of rate is the intrinsic frequency 53.6Hz of the 13rd rank, according to the 13rd rank intrinsic frequency
The corresponding natural mode of vibration of 53.6HZ learns that Oscillation Amplitude maximum position i.e. position one is the second turn of bilge of air intake duct 53, direction of vibration edge
The tangential direction of compressor casing circumferential direction.
It takes and the second turn of bilge of air intake duct 53 is moved up into 20mm, and where reducing 51 observation point one of the first turn of bilge of air intake duct
Arc radius, not only reduced the position one i.e. quality of the second turn of bilge of air intake duct 53 in this way but also increased rigid on its direction of vibration
Degree.
Piping options after optimization are re-started into simulation analysis, compressor piping system after being optimized as shown in Figure 10
In observation point one stress frequency response curve and observation point two after optimization in compressor piping system as shown in figure 11
Stress frequency response curve, crest frequency corresponding to each peak stress is 35Hz and 68Hz in harmonic responding analysis result, with
The least absolute value of the working frequency 50Hz of compressor is the 8HZ that 15Hz is greater than in harmonic responding analysis evaluation criterion, peak stress
The corresponding frequency of 0.618 times of value of the amplitude of 35Hz and 68Hz is respectively the difference of the working frequency of 38Hz and 65Hz and compressor
Least absolute value be that 12Hz is not less than 6Hz, therefore the compressor piping in d can be entered step and carry out trial-production processing.
Claims (10)
1. the simulation optimization method of air-conditioner with fixed frequency compressor piping vibration, which comprises the following steps:
A. the finite element model for determining compressor piping system and the observation point on finite element model；
B. is applied by boundary condition and carries out model analysis to it for finite element model and obtain the intrinsic frequency and phase of finite element model
Corresponding natural mode of vibration, to finite element model apply boundary condition and load motivate and it is carried out harmonic responding analysis obtain it is described
The stress frequency response curve of observation point；
C. frequency corresponding to peak stress is denoted as crest frequency, humorous sound in judgment step b in identified sign frequency response curve
Whether the result that should be analyzed, which meets piping harmonic responding analysis evaluation criterion, carries out step d if meeting, and otherwise, enters step e；
D. compressor piping carries out trial-production processing；
E. it chooses with the smallest crest frequency of difference absolute value of the working frequency of compressor and the crest frequency is denoted as peak value frequently
Rate one is chosen and the smallest intrinsic frequency of difference absolute value of crest frequency one and obtains the corresponding intrinsic vibration of the intrinsic frequency
Type remembers that the natural mode of vibration is natural mode of vibration one, determines that Oscillation Amplitude is maximum in finite element model according to the natural mode of vibration one
The direction of vibration at position and the position, the position are denoted as position one；
F. the quality at position one is adjusted；And/or rigidity of the adjustment position one on the direction of vibration, enter step b.
2. the simulation optimization method of air-conditioner with fixed frequency compressor piping vibration as described in claim 1, which is characterized in that described
In step f, if the crest frequency one is greater than the working frequency of compressor, reduce the quality at the position one, and/or,
Increase rigidity of the position one on the direction of vibration；If the crest frequency one is less than the working frequency of compressor, increase
Quality at the position one, and/or, reduce rigidity of the position one on the direction of vibration.
3. the simulation optimization method of air-conditioner with fixed frequency compressor piping vibration as claimed in claim 1 or 2, which is characterized in that
In the step e, when the working frequency of compressor is greater than the minimum value of the crest frequency and is less than the maximum value of crest frequency
When, if the crest frequency one be greater than the working frequency, also choose be less than working frequency and and working frequency difference it is absolute
It is worth the smallest crest frequency and the crest frequency is denoted as crest frequency two, if crest frequency one is less than the working frequency,
Also choose be greater than working frequency and and working frequency the smallest crest frequency of difference and the crest frequency is denoted as crest frequency two,
In the presence of crest frequency two, also choose and crest frequency two the smallest intrinsic frequency of difference absolute value and obtain the intrinsic frequency
Corresponding natural mode of vibration is remembered that the natural mode of vibration is natural mode of vibration two, is determined in finite element model according to the natural mode of vibration two
The direction of vibration at the maximum position of Oscillation Amplitude and the position, the position are denoted as position two；
If the position two and the position one are inconsistent, step f further includes adjusting as follows: if the crest frequency two is greater than
The working frequency of compressor then reduces the quality at the position two, and/or, increase position two on the direction of vibration
Rigidity；If the crest frequency two is less than compressor operating frequency, increase the quality at the position two, and/or, reduction portion
Rigidity of the position two on the direction of vibration.
4. the simulation optimization method of air-conditioner with fixed frequency compressor piping vibration as described in claim 1, which is characterized in that described
In step a, finite element model includes compressor casing, four-way valve, the fluid reservoir being connected with compressor casing, fixing compressor cylinder
The Rubber foot of body, be connected to the air entry of fluid reservoir with the air intake duct of four-way valve, be connected to the exhaust outlet and four-way valve of compressor casing
Exhaust pipe, the connecting tube one for connecting four-way valve and heat exchanger and the connecting tube two for connecting four-way valve and shut-off valve,
The connecting tube one includes boundary nozzle one and boundary nozzle two, and the connecting tube two includes boundary nozzle three, and compressor includes
Compressor casing and fluid reservoir.
5. the simulation optimization method of air-conditioner with fixed frequency compressor piping vibration as claimed in claim 4, which is characterized in that described
Air intake duct includes outwardly extending the first extension of air intake duct of air entry, connection first extension of air intake duct from fluid reservoir
The first turn of bilge of air intake duct of end bend is extended from the end of first turn of bilge of air intake duct with being parallel to the air intake duct first
The suction of the second extension of air intake duct and connection the second extension of air intake duct end bend that the extending direction receipt in portion extends
The second turn of bilge of tracheae；
The exhaust pipe includes from outwardly extending the first extension of exhaust pipe of exhaust outlet of compressor casing, the connection exhaust
The first turn of bilge of exhaust pipe of pipe the first extension end bend, from the end of first turn of bilge of exhaust pipe to be parallel to the row
The second extension of exhaust pipe and connection second extension of exhaust pipe that the extending direction receipt of the first extension of tracheae extends
The second turn of bilge of exhaust pipe of end bend；
The observation point includes at least observation point one and observation point two, and the observation point one is located at the first turn of bilge of air intake duct and close
At the first extension of air intake duct, the observation point two is located at the first turn of bilge of exhaust pipe and close to the first extension of exhaust pipe.
6. the simulation optimization method of air-conditioner with fixed frequency compressor piping vibration as claimed in claim 4, which is characterized in that step
In b, the boundary condition is the fixation staff cultivation and boundary nozzle one, boundary nozzle two and boundary nozzle three of rubber foot plate surface
Fixed constraint, the Rubber foot are three.
7. the simulation optimization method of air-conditioner with fixed frequency compressor piping vibration as described in claim 1, which is characterized in that step
In b, the load is actuated to two node unit displacement load, and two node is symmetric displacement side on compressor casing
To opposite and carrier phase shift 180 degree.
8. the simulation optimization method of air-conditioner with fixed frequency compressor piping vibration as described in claim 1, which is characterized in that step
In b, preceding 20 rank intrinsic frequency that the model analysis is piped and intrinsic vibration corresponding with the preceding 20 rank intrinsic frequency
Type.
9. the simulation optimization method of air-conditioner with fixed frequency compressor piping vibration as described in claim 1, which is characterized in that step
In b, the harmonic responding analysis method is complete method, and the initial value that frequency is analyzed in the complete method is the work frequency of compressor
Rate subtracts 20Hz, analyzes the stop value of frequency as the working frequency of compressor and adds 20Hz.
10. the simulation optimization method of air-conditioner with fixed frequency compressor piping vibration as described in claim 1, which is characterized in that step
In rapid c, the piping harmonic responding analysis evaluation criterion are as follows: the minimum of the difference of the working frequency of the crest frequency and compressor is absolutely
8Hz is not less than to value, and 0.618 times of the amplitude of peak stress is worth the difference of the working frequency of corresponding frequency and compressor
Least absolute value is not less than 6Hz.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810827978.3A CN109002619A (en) | 2018-07-25 | 2018-07-25 | The simulation optimization method of air-conditioner with fixed frequency compressor piping vibration |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810827978.3A CN109002619A (en) | 2018-07-25 | 2018-07-25 | The simulation optimization method of air-conditioner with fixed frequency compressor piping vibration |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN109002619A true CN109002619A (en) | 2018-12-14 |
Family
ID=64596299
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810827978.3A Pending CN109002619A (en) | 2018-07-25 | 2018-07-25 | The simulation optimization method of air-conditioner with fixed frequency compressor piping vibration |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109002619A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110260454A (en) * | 2019-06-10 | 2019-09-20 | 珠海格力电器股份有限公司 | A kind of load recognition method, device, storage medium and compressor |
| CN110674560A (en) * | 2019-09-24 | 2020-01-10 | 重庆美的通用制冷设备有限公司 | Pipeline vibration control method, computer equipment, storage medium and pipeline system |
| CN111120312A (en) * | 2019-12-13 | 2020-05-08 | 珠海格力电器股份有限公司 | Design method of screw compressor and screw compressor |
| CN111881605A (en) * | 2020-07-24 | 2020-11-03 | 四川长虹空调有限公司 | Automatic optimization design method for variable frequency air conditioner compressor pipeline |
| CN113218049A (en) * | 2021-05-12 | 2021-08-06 | 四川长虹空调有限公司 | Method for quickly matching compressor and pipeline of variable frequency air conditioner |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20150308936A1 (en) * | 2014-04-29 | 2015-10-29 | Livermore Software Technology Corporation | Frequency Domain Structural Analysis Of A Product Having Frequency-Dependent Material Property |
| CN106529048A (en) * | 2016-11-11 | 2017-03-22 | 四川长虹空调有限公司 | Pipe vibration simulation method for air conditioner compressor |
| CN107133419A (en) * | 2017-05-26 | 2017-09-05 | 四川长虹空调有限公司 | Air-conditioner hose system design complete period evaluation of vibration method |
| CN107808056A (en) * | 2017-10-30 | 2018-03-16 | 四川长虹空调有限公司 | Compressor of air conditioner pipe arrangement vibration reliability appraisal procedure |
-
2018
- 2018-07-25 CN CN201810827978.3A patent/CN109002619A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20150308936A1 (en) * | 2014-04-29 | 2015-10-29 | Livermore Software Technology Corporation | Frequency Domain Structural Analysis Of A Product Having Frequency-Dependent Material Property |
| CN106529048A (en) * | 2016-11-11 | 2017-03-22 | 四川长虹空调有限公司 | Pipe vibration simulation method for air conditioner compressor |
| CN107133419A (en) * | 2017-05-26 | 2017-09-05 | 四川长虹空调有限公司 | Air-conditioner hose system design complete period evaluation of vibration method |
| CN107808056A (en) * | 2017-10-30 | 2018-03-16 | 四川长虹空调有限公司 | Compressor of air conditioner pipe arrangement vibration reliability appraisal procedure |
Non-Patent Citations (2)
| Title |
|---|
| 胡洁义等: "某乘用车空调管路疲劳失效原因分析", 《合肥工业大学学报（自然科学版）》 * |
| 陈超宇等: "空调配管动态特性研究", 《电子科技》 * |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110260454A (en) * | 2019-06-10 | 2019-09-20 | 珠海格力电器股份有限公司 | A kind of load recognition method, device, storage medium and compressor |
| CN110674560A (en) * | 2019-09-24 | 2020-01-10 | 重庆美的通用制冷设备有限公司 | Pipeline vibration control method, computer equipment, storage medium and pipeline system |
| WO2021056977A1 (en) * | 2019-09-24 | 2021-04-01 | 重庆美的通用制冷设备有限公司 | Pipeline vibration control method, computer device, storage medium and pipeline system |
| CN111120312A (en) * | 2019-12-13 | 2020-05-08 | 珠海格力电器股份有限公司 | Design method of screw compressor and screw compressor |
| CN111881605A (en) * | 2020-07-24 | 2020-11-03 | 四川长虹空调有限公司 | Automatic optimization design method for variable frequency air conditioner compressor pipeline |
| CN111881605B (en) * | 2020-07-24 | 2022-12-16 | 四川长虹空调有限公司 | Automatic optimization design method for variable frequency air conditioner compressor pipeline |
| CN113218049A (en) * | 2021-05-12 | 2021-08-06 | 四川长虹空调有限公司 | Method for quickly matching compressor and pipeline of variable frequency air conditioner |
| CN113218049B (en) * | 2021-05-12 | 2022-04-01 | 四川长虹空调有限公司 | Method for quickly matching compressor and pipeline of variable frequency air conditioner |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN109002619A (en) | The simulation optimization method of air-conditioner with fixed frequency compressor piping vibration | |
| CN105243172B (en) | A kind of Engine Mounting System optimization method considering dynamic rate and dynamic antivibration | |
| CN108763715A (en) | The method of tire of air-conditioner with fixed frequency compressor piping vibration | |
| CN106351824B (en) | Air compressor machine energy valid value test method and test macro based on Internet of Things big data | |
| CN109063312B (en) | Vibration simulation method for piping system of double-rotor compressor of variable frequency air conditioner | |
| CN201392266Y (en) | Oscillation testing bench of automotive vehicle hose | |
| CN110427677A (en) | Bend pipe structure Fast design method in a kind of aero-engine external pipeline system | |
| CN104260802B (en) | The matching process of a kind of longitudinal power assembly suspension system and system | |
| Huang et al. | Optimal design of fluidic diode for valveless piezoelectric pump based on entropy production theory | |
| CN116522480A (en) | Pipeline system high-precision flow-induced vibration calculation method | |
| CN109145498B (en) | Pipeline airflow pulsation calculation method of compressor system | |
| CN105205197B (en) | A kind of oscillation damping method of air-conditioner outdoor unit tonifying Qi pipeline | |
| CN107091218A (en) | Cooler compressor suction conduit assembly mounting structure | |
| CN203835871U (en) | Buffer tank | |
| Kerswell et al. | Steady nonlinear waves in diverging channel flow | |
| CN102237746A (en) | Balance structure of rotary compressor and rotary compressor comprising same | |
| CN204900223U (en) | Test fixture of engine oil pump | |
| CN110239491B (en) | Vehicle cleaning method and system | |
| CN208203586U (en) | Multi-angle transformation pump and its pump body structure | |
| CN105201792A (en) | Spring-type valve-bearing piezoelectric pump | |
| CN215980750U (en) | Damping device for gearbox system and gearbox system | |
| CN106382418B (en) | A kind of pipeline support and method for arranging with dynamic absorber function | |
| KR100888266B1 (en) | Triplex pulseless metering pump and control method using constant velocity cam | |
| CN204493338U (en) | Diaphragm type hydraulic vibration exciter vibrating table | |
| CN102748272A (en) | Piezoelectric pump and valve block thereof |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20181214 |
|
| RJ01 | Rejection of invention patent application after publication |