CN101956696A - Compressor - Google Patents
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- CN101956696A CN101956696A CN2010102301700A CN201010230170A CN101956696A CN 101956696 A CN101956696 A CN 101956696A CN 2010102301700 A CN2010102301700 A CN 2010102301700A CN 201010230170 A CN201010230170 A CN 201010230170A CN 101956696 A CN101956696 A CN 101956696A
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Abstract
In compressor (1), drive the first pressurized air generating apparatus (13a) positioned opposite to each other and the second pressurized air generating apparatus (13b) based on the rotation of motor (3), generate pressurized air thus and be stored in the storage tank (8).Compressor (1) possesses the rotation driven quantity control device (5) of the rotation driven quantity of controlling described motor (3) and detects the pressure state detection unit (12) of the pressure state in the described storage tank (8).The load that the load that the described first pressurized air generating apparatus (13a) is loaded and the described second pressurized air generating apparatus (13b) are loaded is according to the pressure state of described storage tank (8) and different.When being in the predetermined range by the detected pressure state of described pressure state detection unit (12), to compare when outer with being in predetermined range, described rotation driven quantity control device (5) reduces the rotation driven quantity of described motor (3).Scope before and after the force value of the described storage tank (8) when the described predetermined range of the described pressure state load value that to be the described first pressurized air generating apparatus (13a) load value of being loaded loaded with the described second pressurized air generating apparatus (13b) is consistent.
Description
Technical field
The present invention relates to compressor, more specifically, relate to following compressor: the rotation based on motor drives the first pressurized air generating apparatus positioned opposite to each other and the second pressurized air generating apparatus, generates pressurized air thus, and is stored in the storage tank.
Background technique
Use in the building site under the situation of the driving tool utilize compressed-air actuated nailing maching etc.,, air compressor need be set for driving tool is supplied with pressurized air.Air compressor is following structure: by drive motor portion, utilize the pressurized air generating unit to generate pressurized air, the pressurized air that generates is stored in a jar portion, supply with pressurized air to driving tool thus.
Use under the situation of driving tool using this compressor, produce the tendency of noise (driving sound) when existing in the driving of compressor.Therefore, have following compressor: consideration possesses the operation mode (for example with reference to patent documentation 1) of " silent mode " in the situation that operators such as night carry out operation in order to reduce driving sound.
Patent documentation 1:JP-B2-4203292
In possessing the compressor of silent mode, the rotating speed of the rotating speed that makes motor during with common running compared and reduced and keep certain rotating speed, realizes the reduction of driving sound thus.
Yet, recently in the compressor that utilizes, in order to use a plurality of driving tool simultaneously, or consider to utilize the use of the driving tool of elevated pressures, there is the tendency that the pressure state in the jar is maintained high pressure and tankage size is maximized.Like this pressure in the jar is being maintained in the compressor of high pressure, existing driving sound to become big tendency, requiring further to reduce driving sound.In addition, as mentioned above, in the compressor that tankage size maximizes,, then follow the reduction of rotating speed sometimes and the performance of compressor is reduced if be that purpose is carried out the control that the rotating speed with motor limits lowlyer to reduce driving sound.
Summary of the invention
More than one embodiment of the present invention provides a kind of compressor, and it can be kept to compare with performance more than in the past the silent mode equal extent and with silent mode in the past and reduce driving sound.
According to more than one embodiment of the present invention, compressor 1 is provided, its rotation based on motor 3 drives the first pressurized air generating apparatus 13a positioned opposite to each other and the second pressurized air generating apparatus 13b, generate pressurized air thus, and be stored in the storage tank 8, compressor 1 possesses the rotation driven quantity control device 5 of the rotation driven quantity of controlling described motor 3 and detects the pressure state detection unit 12 of the pressure state in the described storage tank 8.The load that the load that the described first pressurized air generating apparatus 13a is loaded and the described second pressurized air generating apparatus 13b are loaded is according to the pressure state of described storage tank 8 and different.When being in the predetermined range by described pressure state detection unit 12 detected pressure states, the rotation driven quantity that described rotation driven quantity control device 5 makes described motor 3 be in predetermined range and compare minimizing when outer.Scope before and after the force value of the described storage tank 8 when the described predetermined range of the described pressure state load value that to be the described first pressurized air generating apparatus 13a load value of being loaded loaded with the described second pressurized air generating apparatus 13b is consistent.The rotation driven quantity of the motor that reduces when in addition, being in the predetermined range is not zero.In addition, do not comprise zero in the described predetermined range of described force value.
In above-mentioned structure, the first pressurized air generating apparatus and the second pressurized air generating apparatus are set relative to one another, and then make the load value state of changing of the load that the first pressurized air generating apparatus and the second pressurized air generating apparatus loaded separately different according to the pressure state of storage tank.Like this, the different reason of load value state of changing of load is to result from for storage tank is accumulated the pressurized air of authorized pressure effectively and made the compressed capability of the first pressurized air generating apparatus and the compressed capability of the second pressurized air generating apparatus have difference, is the formation that adopts mostly in the general compressor.
In the compressor of this structure, usually, the first pressurized air generating apparatus and the second pressurized air generating apparatus relatively are provided with, therefore when the load value of being loaded at the load value that the first pressurized air generating apparatus is loaded and the second pressurized air generating apparatus is consistent, the compression movement of the compression movement of the first pressurized air generating apparatus and the second pressurized air generating apparatus influences each other, and the acoustic pressure of the driving sound of compressor increases significantly.
Therefore, in the rotation driven quantity control device of the compressor of embodiments of the invention, obtain the pressure state of load value that load value that the first pressurized air generating apparatus loaded and the second pressurized air generating apparatus the loaded storage tank when consistent in advance, by the detected pressure state of pressure state detection unit the pressure state when consistent with the aforesaid load value of obtaining in advance near the time (, in the front and back scope of the pressure state when consistent), the rotation driven quantity (comparing with scope in addition) of motor is reduced.The increase of the acoustic pressure of the driving sound of the compressor that consequently, the rotation that can suppress motor drives, the compression movement of the first pressurized air generating apparatus and the compression movement of the second pressurized air generating apparatus etc. cause.
In addition, the described rotation driven quantity of the described motor that reduces in the described rotation driven quantity control device also can be the rotation driven quantity that is set at following degree: make the acoustic pressure of the driving sound that carries out the compressor after this minimizing keep the acoustic pressure of the driving sound of the compressor before reducing.
Like this, so that carry out the degree of acoustic pressure that the acoustic pressure of the driving sound of the compressor after the minimizing of motor rotation driven quantity is kept the driving sound of the compressor before the minimizing of carrying out motor rotation driven quantity, the rotation driven quantity of motor is reduced, not only can reduce the driving sound that load value that load value that the first pressurized air generating apparatus loaded and the second pressurized air generating apparatus loaded can rise when consistent thus energetically, operator is waited be difficult to the sound pressure variations of recognizing the driving sound before and after the rotation driven quantity that reduces motor.Therefore, can reduce the operator recognizes because of sound pressure variations etc. and the situation of driving sound can suppress to hear that the operator of driving sound feels noisy situation.
In the rotation driven quantity control device of the compressor of embodiments of the invention, in the time of in the predetermined range of the front and back of the pressure state that is in load value that load value that the first pressurized air generating apparatus loaded and the second pressurized air generating apparatus the loaded storage tank when consistent by the detected pressure state of pressure state detection unit, reduce the rotation driven quantity of motor energetically, can suppress the increase of acoustic pressure of the driving sound of compressor thus.
Description of drawings
Fig. 1 is the block diagram that the summary of the air compressor of expression exemplary embodiments constitutes.
Fig. 2 is the sectional drawing of the formation of expression air compressing mechanism portion of exemplary embodiments and motor part.
Fig. 3 represents the figure that the load value of the piston load relevant with the first air compressing mechanism portion of exemplary embodiments and the second air compressing mechanism portion changes according to the variation in pressure in the jar portion.
Fig. 4 is the block diagram of control circuit portion of the air compressor of expression exemplary embodiments.
Fig. 5 is the figure of variation of acoustic pressure of driving sound of acoustic pressure, the air compressor when with the rotating speed of using with normal mode motor part being driven of the driving sound of the air compressor when representing that according to the force value of jar portion the rotating speed of the motor part of exemplary embodiments is 1000rpm～1800rpm.
Fig. 6 is the figure of variation of acoustic pressure of the driving sound of the air compressor when representing that according to the force value of jar portion the rotating speed of the motor part of exemplary embodiments is 1500rpm, 1800rpm～2200rpm.
Fig. 7 is the flow chart of processing of microprocessor of the control circuit portion of expression exemplary embodiments.
Fig. 8 is to be the figure that the situation of 2.0MPa, the situation that is set at the situation of 2.25MPa and is set at 2.5MPa compare the state of changing of representing driving sound to the design of pressure in the jar portion that the rotating speed of motor part is reached 1500rpm in the air compressor of exemplary embodiments.
Fig. 9 is the figure that represents the rotating speed of the motor part under normal mode, silent mode and the super-silent pattern of the air compressor of exemplary embodiments according to the force value in the jar portion.
Figure 10 is the figure of acoustic pressure that represents the driving sound of the air compressor under normal mode, silent mode and the super-silent pattern of the air compressor of exemplary embodiments according to the force value in the jar portion.
Embodiment
Below, as an example of compressor of the present invention, utilize accompanying drawing that air compressor is at length described.
Fig. 1 is the block diagram that the summary of the air compressor of expression exemplary embodiments constitutes.Air compressor 1 roughly is made of jar portion 2, motor part (motor) 3, pressurized air generating unit (the first pressurized air generating apparatus, the second pressurized air generating apparatus) 4 and control circuit portion (rotation driven quantity control device) 5.
Be provided with a plurality of pressurized air conveying ends 9 at storage tank 8.In the air compressor 1 of exemplary embodiments, be provided with and be used to the compressed-air actuated normal pressure conveying end 9b that takes out the compressed-air actuated high pressure conveying end 9a of high pressure and be used to take out normal pressure, at high pressure conveying end 9a, the compressed-air actuated pressure that is taken out by reduction valve 10a is decompressed to 1.5MPa～2.50MPa degree, at normal pressure conveying end 9b, the compressed-air actuated pressure that is taken out by reduction valve 10b is decompressed to 0.7MPa～1.5MPa degree.In addition, in order to supply with to driving tool such as nailing machings, can set up, unload steam hose (diagram is omitted) at each conveying end 9a, 9b by the pressurized air of reduction valve 10a, 10b decompression.
In addition, in storage tank 8, be provided with the pressure transducer (pressure state detection unit) 12 that is used to detect the pressure in the storage tank 8.The pressure cell that pressure transducer 12 has by inside is converted to the function of electrical signal with the variation in pressure in the storage tank 8, and detected electrical signal is passed to control circuit portion 5.
Pressurized air generating unit 4 is following structure: have the air compressing mechanism portion 13 that roughly is made of piston and cylinder, make the reciprocating motion of the pistons that is provided with in cylinder, will be incorporated into the air compression in the cylinder from the Aspirating valves of cylinder, thereby generate pressurized air.
In the general pressurized air generating unit (the pressurized air generating unit 4 that comprises exemplary embodiments), as shown in Figure 2, be provided with two air compressing mechanism portions 13 that roughly constitute by piston and cylinder.The 13a of the first air compressing mechanism portion (the first pressurized air generating apparatus) that constitutes a side air compressing mechanism portion 13 is that the first cylinder 14a and the first piston 15a that 60mm and stroke are defined as 25mm constitutes by cylinder bore, and the 13b of the second air compressing mechanism portion (the second pressurized air generating apparatus) that constitutes the opposing party's air compressing mechanism portion 13 is that the second cylinder 14b and the second piston 15b that 40mm and stroke are defined as 10mm constitutes by cylinder bore.
In addition, motor part 3 as shown in Figure 2 with the 4 adjacent settings of pressurized air generating unit, make the structure of running shaft 19 rotations of motor part 3 when rotating as mentioned above for the rotor 17 of motor part 3.It is rotatably mounted with bearing 20a, 20b that the running shaft 19 of motor part 3 is rotated axle, link the connecting rod 21a that first piston 15a is arranged via the 22a of bearing portion (crank bearing) on the running shaft 19, in addition, the connecting rod 21b of the second piston 15b is linked on the running shaft 19 via the 22b of bearing portion (crank bearing).And the end of running shaft 19 is provided with the fan 23 that is used to import extraneous gas.
When the running shaft 19 of motor part 3 begins to rotate, the first piston 15a of first 13a of air compressing mechanism portion is accompanied by the advance and retreat mobile (piston motion) in the first cylinder 14a that are rotated in of running shaft 19, carry out the compression of the air in the first cylinder 14a, in addition, the second piston 15b of second 13b of air compressing mechanism portion is accompanied by the advance and retreat mobile (piston motion) in the second cylinder 14b that are rotated in of running shaft 19, carries out the compression of the air in the second cylinder 14b.
Herein, the first cylinder 14a cylinder bore of first 13a of air compressing mechanism portion is 60mm, stroke is defined as 25mm, relative therewith, the first piston 15a cylinder bore of second 13b of air compressing mechanism portion is 40mm, stroke is defined as 10mm, in first 13a of air compressing mechanism portion the pressure state of compressed air and in second 13b of air compressing mechanism portion the pressure state of compressed air dissimilate.Therefore, in the pressurized air generating unit 4 of air compressor 1, in first 13a of air compressing mechanism portion with air compression after, the compression that compressed air in first 13a of air compressing mechanism portion further utilizes second 13b of air compressing mechanism portion to form high pressure is handled, can be carried out the pressure control in jar portion 2 thus effectively.
In addition, as mentioned above, for the first cylinder 14a and the second cylinder 14b, cylinder bore and stroke difference, the piston load that puts on the first piston 15a and the second piston 15b respectively also is different values.Fig. 3 represents that according to the variation in pressure in the jar portion 2 load value of the piston load relevant with second 13b of air compressing mechanism portion with first 13a of air compressing mechanism portion changes the figure of (load value state of changing).
As shown in Figure 3, when the force value in the storage tank 8 is low (for example 0MPa～0.6MPa degree), first 13a of air compressing mechanism portion is applied positive load and the pressure in jar portion 2 are risen, but the load that puts on first 13a of air compressing mechanism portion becomes the state that culminates because of the ability of first 13a of air compressing mechanism portion in predetermined value (being about 160kgf degree in the exemplary embodiments).
After the load of first 13a of air compressing mechanism portion reaches predetermined value, utilize second 13b of air compressing mechanism portion that compressed air in first 13a of air compressing mechanism portion is compressed, improve the pressure in the jar portion 2 thus.Therefore, the load that puts on second 13b of air compressing mechanism portion is compared increase lentamente with first 13a of air compressing mechanism portion, surpass the predetermined value (about 160kgf) of first 13a of air compressing mechanism portion, rises pro rata with the pressure rising in the jar portion 2.
Compressed air is supplied with to the storage tank 8 of jar portion 2 via connecting pipe 14 (with reference to Fig. 1) in second 13b of air compressing mechanism portion.
The rectification circuit 28 of converter circuit 26 and smoothing circuit 30 have by to carry out rectification/smoothly convert to the function of VDC as the ac power supply 31 of the driving source of air compressor 1.Be provided with switching element 29a in the inside of booster circuit 29, have the function of carrying out the amplitude control of VDC according to the control command of microprocessor 25.Booster circuit 29 is controlled via the boost pressure controller 32 of the PAM instruction of accepting microprocessor 25.
Detected force value information in the pressure transducer 12 of microprocessor 25 inputs in jar portion 2.In addition, microprocessor 25 is can be to the formation of converter circuit 26 and converter circuit 27 output control informations (PAM instruction, PWM instruction).
In converter circuit 26 and the converter circuit 27, the drive controlling of coming operating motor portion 3 based on control information by microprocessor 25 output.Particularly, microprocessor 25 via the switching element 29a of boost pressure controller 32 control booster circuits 29, carries out the drive controlling of converter circuit 26 by to boost pressure controller 32 output PAM instructions.In addition, similarly, the control of converter circuit 27 is carried out in the 27 output PWM instructions of 25 pairs of converter circuits of microprocessor thus.
Then, the sound pressure variations for the driving sound of the air compressor of obtaining according to the rotating speed of motor part 31 describes.
The figure of the variation of the acoustic pressure of the driving sound of the air compressor 1 when Fig. 5 is the acoustic pressure of driving sound of the air compressor 1 when representing that according to the force value of jar portion 2 rotating speed of motor part 3 is 1000rpm, 1100rpm, 1200rpm, 1300rpm, 1400rpm, 1500rpm, 1600rpm, 1700rpm and 1800rpm and the rotating speed drive motor portion 3 that uses with normal mode.
In addition, the state that the rotating speed of motor part 3 is maintained 1800rpm is equivalent to the drive condition under the silent mode of air compressor 1.In addition, Fig. 5 be illustrated in the state of driving voltage being set/maintained 100V, the data the when acoustic pressure that drives sound in the position of fan 23 sides of motor part 3 is measured.
As shown in Figure 5, during with each rotating speed drive motor portion 3 from 1000rpm to 1800rpm, compare during with drive motor portion 3 under normal mode, acoustic pressure reduces.In addition, the force value in jar portion 2 reach before the 1.5MPa degree during, under the whole rotating speed from 1000rpm to 1800rpm, the mitigation (variation less state) that becomes of the sound pressure variations of driving sound.
But the force value in jar portion 2 is under the situation of 1600rpm～1800rpm at speed setting when 1.5MPa is increased to 2.5MPa, increases tendency with the acoustic pressure of the driving sound of (reach 1.5MPa degree before) before this and compares, and acoustic pressure rises sharp.And the force value in the jar portion 2 is in the motor part 3 of 1600rpm～1800rpm from above near the 2.5MPa at speed setting, shows the tendency that acoustic pressure is kept or reduce a little.
On the other hand, be that 1500rpm is when following with speed setting, as shown in Figure 5, show with jar portion 2 in force value irrespectively (also be) tendency that the acoustic pressure of driving sound increases lentamente under the situation from 1.5MPa to 2.5MPa, be not absorbed in as with speed setting being the situation that acoustic pressure that 1600rpm drives when above rises sharp.
Therefore, we can say, even using in the past silent mode (rotating speed of motor part 3 be about 1800rpm) also to have in the scope of the force value more than the 1.5MPa of the big tendency of driving sound change, making the rotation of motor part 3 be reduced to the rotating speed of the rising that does not produce rapid driving sound, is effective for the acoustic pressure that reduces driving sound.Particularly, can judge as follows: as shown in Figure 5,, the rotating speed of motor part 3 is reduced, thereby can realize reducing the acoustic pressure of driving sound at the rotating speed of the rising that does not produce rapid driving sound and before showing the 1500rpm of the highest rotating speed therein.
In addition, before the force value in jar portion 2 becomes 1.5MPa during, under the whole rotating speed from 1000rpm to 1700rpm, demonstrate the proportional and tendency of increase lentamente of force value in driving sound and jar portion 2.If consider this increase slowly, be the rotating speed higher then than 1500rpm by speed setting with motor part 3, even the change of the force value in the jar portion 2, the acoustic pressure change that also is difficult to produce driving sound can reduce driving sound variation acoustically.
Fig. 6 is the figure of variation of acoustic pressure of the driving sound of the air compressor 1 when representing that according to the force value of jar portion 2 rotating speed of motor part 3 is 1500rpm, 1800rpm, 1900rpm, 2000rpm, 2100rpm and 2200rpm.In addition, Fig. 6 is also the same with Fig. 5, the data the when acoustic pressure that be illustrated in the state of driving voltage being set/maintained 100V, drives sound in the position of fan 23 sides of motor part 3 is measured.
According to Fig. 6 as can be known, in the motor part 3 of having set the rotating speed from 1800rpm to 2200rpm respectively, identical with Fig. 5, force value in jar portion 2 is increased under the situation of 2.5MPa from 1.5MPa, compare with the increase tendency of the acoustic pressure of (the 1.5MPa degree is following) before this, show the tendency that acoustic pressure rises sharp.In addition, as shown in Figure 6, be in the motor part 3 of 1500rpm at rotating speed, compare with the motor part 3 more than the 1800rpm, keep the relative state that reduces of acoustic pressure of driving sound.
On the other hand, before the force value in jar portion 2 reaches 1.5MPa during, the acoustic pressure of each motor part 3 that is set at the rotating speed of 1500rpm, 1800rpm, 1900rpm demonstrate closer like sound pressure level.Therefore, before the force value in jar portion 2 reaches 1.5MPa during, even the rotating speed 1800rpm of the motor part under the silent mode 3 is reduced to 1500rpm etc., can not obtain the effect that acoustic pressure reduces energetically, on the contrary, even rotating speed rises to 1900rpm, driving sound can not enlarge markedly yet.
Especially, the acoustic pressure of the driving sound of the air compressor 1 during before reaching 1.5MPa for the force value in jar portion 2, preferably being maintained with force value in jar portion 2 is the identical degree of acoustic pressure of the driving sound of the air compressor 1 of 2.5MPa when the speed setting of motor part 3 being 1500rpm when above.Like this, by the force value in the jar portion 2 are reached before the 1.5MPa during acoustic pressure and the force value in jar portion 2 of driving sound be that the acoustic pressure of the driving sound of 2.5MPa when above maintains same degree, operator is waited be difficult to the sound pressure variations of driving sound of the front and back of the rotation driven quantity of recognizing the reduction motor part.Therefore, can reduce the operator recognizes because of sound pressure variations etc. and the situation of driving sound can suppress to hear that the operator of driving sound feels noisy situation.
Consider these aspects, consider in addition that the performance of jar portion 2 is kept/improve, can judge: determine force value in jar portion 2 reach 1.5MPa before during the rotating speed of motor part 3 time, be 1900rpm preferably with speed setting.
Like this, in the air compressor 1 of exemplary embodiments, when the rotating speed of each motor part 3 was asked for the driving sound state of the air compressor 1 that changes according to the force value of jar portion 2, the interior pressure that has a jar portion 2 is the temporary transient tendency of increase from about 1.5MPa to about 2.5MPa.As its reason, can think because toward each other and the compression movement of the compression movement of horizontally disposed first 13a of air compressing mechanism portion and second 13b of air compressing mechanism portion influences each other and produces vibration etc.
The air compressing mechanism portion of two cylinders that the level as described above that possesses general compressor relatively disposes.These two air compressing mechanism portions are in order to reduce the pressure in the jar portion 2 respectively effectively, pressure with extraneous gas in a side air compressing mechanism portion is reduced to certain value, then, in the opposing party's air compressing mechanism portion, the air of air compressing mechanism portion compression that will be by a side further compresses, and thus the pressure in the jar portion 2 is brought up to the force value of expectation and keeps.
In the air compressor 1 of exemplary embodiments, first 13a of air compressing mechanism portion that carries out the compression of extraneous gas at first compares with second 13b of air compressing mechanism portion that the air that is compressed by first 13a of air compressing mechanism portion is further compressed processing, cylinder bore and stroke amount are bigger, for first 13a of air compressing mechanism portion and second 13b of air compressing mechanism portion, its compression performance (compressed capability) difference.The figure that its poor performance is represented as an example is above-mentioned Fig. 3.
As shown in Figure 3, under the situation that the pressure in making jar portion 2 rises, the load value of the piston load of the variation of the load value of the piston load of first 13a of air compressing mechanism portion and second 13b of air compressing mechanism portion changes different respectively.If note the load value of the piston load of each air compressing mechanism portion, then in first 13a of air compressing mechanism portion and second 13b of air compressing mechanism portion of the air compressor 1 of exemplary embodiments, comparing second 13b of air compressing mechanism portion at the air compressor 1 firm load value that starts the piston load of back first 13a of air compressing mechanism portion rises sharp, when the interior pressure in the jar portion 2 reached 0.6MPa, load value reached about 160kgf and becomes the state (keeping the state of about 160kgf) that culminates.
On the other hand, about second 13b of air compressing mechanism portion, the load value of piston load is compared the rising of the load value of first 13a of air compressing mechanism portion and is risen lentamente.Second 13b of air compressing mechanism portion of the air compressor 1 of exemplary embodiments demonstrates according to the pressure in the jar portion 2 and rises and the tendency of piston load rising.Different according to the load value rising characteristic of the load value rising characteristic (load value state of changing) of this first air compressing mechanism 13a of portion and second 13b of air compressing mechanism portion, in the air compressor 1, when air compressor 1 starting, carrying out the compression of first 13a of air compressing mechanism portion apace handles, press in jar portion 2 under the state that rises to a certain degree, the main body that compression is handled shifts to second 13b of air compressing mechanism portion from first 13a of air compressing mechanism portion, thereafter the jar portion 2 of successfully carrying out thus interior in press liter.
In the variation of the piston load of this first air compressing mechanism 13a of portion and second 13b of air compressing mechanism portion, the force value of jar portion 2 when each load value is consistent is 1.5MPa in the air compressor 1 of exemplary embodiments, and (for example 1.0MPa～2.0MPa) is equivalent to the prespecified range of the interior force value of jar portion that the acoustic pressure of motor part 3 begins to rise 2 to the value of the front and back of this force value.
Can be judged as this be because: under first 13a of the air compressing mechanism portion state consistent with the load value of the piston load of second 13b of air compressing mechanism portion, the piston motion of the piston motion of first 13a of air compressing mechanism portion and second 13b of air compressing mechanism portion interacts, the influence in the gap of the bearing of supporting motor portion 3, first 13a of air compressing mechanism portion and second 13b of air compressing mechanism portion, support material etc. becomes maximum, and it is big that vibration etc. become.Therefore, can be judged as in the force value in the producible jar of the influence that this piston motion brings portion 2, have the driving statement tendency clear of air compressor 1.
Therefore, in the air compressor 1 of exemplary embodiments, in control circuit portion 5, obtain the interior pressure in the piston load of first 13a of the air compressing mechanism portion jar portion consistent 2 in advance with the piston load of second 13b of air compressing mechanism portion, force value based on this jar portion 2, change the control of the rotation status of motor part 3, realize reducing the processing of the driving sound of air compressor 1 thus.
Fig. 7 is the flow chart of processing of the microprocessor 25 of expression control circuit portion 5.Microprocessor 25 is carried out the processing of flow chart shown in Figure 7 according to the control program of middle storages such as ROM.
Then, microprocessor 25 is obtained force value (step S.3) in jar portion 2 via pressure transducer 12.Then, microprocessor 25 judges that whether the interior force value of jar portions 2 is the value (step S.4) greater than 1.5MPa.Force value in jar portion 2 be not during greater than the value of 1.5MPa (more than the 0Pa and 1.5MPa when following, step S.4 in during for "No"), microprocessor 25 maintains 1900rpm (step S.1) with the rotating speed of motor part 3, carry out the drive controlling (step S.2) of motor part 3, obtain the force value (step S.3) in jar portion 2 once more, judge that whether the interior force value of jar portion 2 is the value (step S.4) greater than 1.5MPa.
Force value in the jar portion 2 be (step S.4 in for "Yes" time) during greater than the value of 1.5MPa, and microprocessor 25 judges that whether the interior force value of jar portions 2 is the value (step S.5) less than 2.5MPa.Force value in the jar portion 2 are not (when 2.5MPa is above, when step is "No" in S.5) during less than the value of 2.5MPa, and microprocessor 25 is 1500rpm (step S.6) with the speed setting of motor part 3.Then, microprocessor 25 carries out the drive controlling (step S.2) of motor part 3 so that the rotating speed of motor part 3 is the mode of 1500rpm.Whether then, microprocessor 25 is obtained the force value (step S.3) in jar portion 2 as mentioned above, repeats force value in jar portion 2 greater than the judgement (step S.4) of the value of 1.5MPa.
On the other hand, force value in the jar portion 2 be (force value in jar portion 2 are, when step is "Yes" in S.5) during less than the value of 2.5MPa during greater than the value of 1.5MPa and less than the value of 2.5MPa, and microprocessor 25 is according to the rotating speed (step S.7) of the interior design of pressure motor part 3 of jar portion 2.
Particularly, microprocessor 25 is set the rotating speed of motor part 3 in the following manner: when the force value in jar portion 2 is 1.5MPa, the rotating speed that makes motor part 3 is 1900rpm, rise along with the force value in the jar portion 2 then and the rotating speed of motor part 3 is reduced, when the force value in jar portion 2 reached 2.5MPa, the rotating speed that makes motor part 3 was 1500rpm.That is, in the air compressor 1 of exemplary embodiments, the formation that reduces linearly according to the interior pressures in the jar portion 2 for the rotating speed that makes motor part 3.The rotating speed of the motor part 3 corresponding with the force value in the jar portion 2 can be to be stored in data among the ROM etc. of microprocessor 25 as the table data in advance, in addition, also can be the data that microprocessor 25 is calculated according to the force value in the jar portion 2.
In addition, in the air compressor 1 of exemplary embodiments, adopted following method: when the force value in jar portion 2 is 1.5MPa, with the speed setting of motor part 3 is 1900rpm, when the force value in jar portion 2 is 2.5MPa, is 1500rpm with the speed setting of motor part 3, determine the rotating speed of motor part 3 thus linearly, but the force value that the speed setting of motor part 3 changed in the jar portion 2 of 1500rpm not necessarily are limited to 2.5MPa, also can be 2.0MPa, can also be 2.25MPa.Force value in this jar portion 2 can suitably change by cylinder bore, the stroke amount of first 13a of air compressing mechanism portion and second 13b of air compressing mechanism portion.
Fig. 8 is to be the figure that the situation of 2.0MPa, the situation that is set at the situation of 2.25MPa and is set at 2.5MPa compare the state of changing of representing driving sound to the design of pressure in the jar portion 2 that the rotating speed of motor part 3 is reached 1500rpm in the air compressor 1 of exemplary embodiments.In addition, Fig. 8 is the coordinate diagram of value that is illustrated in the acoustic pressure of the motor part 3 in the processing that fan 23 sides are determined at using charged air pressures in jar portion 2.
In the air compressor 1 of exemplary embodiments, as shown in Figure 8, the sound pressure variations minimum of driving sound when the design of pressure in the jar portion 2 are 2.5MPa, the design of pressure in jar portion 2 when therefore the rotating speed of motor part 3 being reduced to 1500rpm are 2.5MPa, to realize the change of minimizing driving sound.In addition, in the air compressor 1 of exemplary embodiments, the sound pressure variations minimum of driving sound when the design of pressure in the jar portion 2 are 2.5MPa, but the 2.5MPa always not of the force value in jar portion 2 of the sound pressure variations minimum of driving sound, therefore the force value of setting is not limited to 2.5MPa.
As mentioned above, behind the rotating speed (rotating speed of rotor 17) (step S.7) of microprocessor 25 according to the design of pressure motor part 3 in the jar portion 2, to carry out the drive controlling (step S.2) of motor part 3 according to rotating speed rotary driving motor portion 3 modes of having set.After, microprocessor 25 according to the setting that the force value in the jar portion 2 changes the rotating speed of motor part 3, carries out the drive controlling of air compressor 1 by repeating above-mentioned contents processing.
Fig. 9 is the coordinate diagram of the rotating speed of the motor part 3 in the super-silent pattern of representing to propose in the common operation mode of air compressor 1, the silent mode that in the past used and the exemplary embodiments according to the force value in the jar portion 2, and Figure 10 is the coordinate diagram of acoustic pressure of representing the driving sound of the air compressor 1 in above-mentioned three patterns according to the force value in the jar portion 2.
As shown in Figure 9, under the common operation mode of air compressor 1, the rotating speed of motor part 3 changes according to the force value in the jar portion 2, but for this rotation speed change, microprocessor 25 is not to control according to the force value in the jar portion 2, but control the rotating speed of motor part 3, so can not carry out control energetically based on the force value in the jar portion 2 according to the power value of ac power supply 31.Under common operation mode,, consider the tolerance of power value and the control of the rotating speed of highland setting motor part 3 slightly in order to improve the force value jar portion 2 in when the starting of air compressor 1 as soon as possible.Therefore, there is not actively to consider the acoustic pressure of reduction motor part 3.
Under silent mode,, therefore the rotating speed of motor part 3 is set in 1800rpm all the time and turns round regardless of the force value in the jar portion 2 owing to the driving sound with reduction air compressor 1 is first target.On the other hand, under the super-silent pattern that in exemplary embodiments, proposes, to 1.5MPa, be 1900rpm with the speed setting of motor part 3, between 1.5MPa～2.5MPa, the rotating speed of motor part 3 is reduced linearly, and the speed setting with motor part 3 after 2.5MPa is that 1500rpm turns round.
Under three each operation modes, the driving sound when turning round if will set the rotating speed of motor part 3 as mentioned above compares like this, and then as shown in figure 10, the driving sound when driving under normal mode demonstrates peak.On the other hand, comparing acoustic pressure when driving under driving sound and the normal mode when being driven under silent mode reduces, acoustic pressure rises sharp between the 2.5MPa but the pressure in jar portion 2 becomes from 1.5MPa, therefore worry that the operator can be appreciated that the noise of air compressor 1 and feels noisy because of the force value jar portion 2 in is that the driving sound of 1.5MPa generation when following and the force value in the jar portion 2 are the acoustic pressure difference between the driving sound of 2.5MPa generation when above etc.
But, under super-silent pattern, as shown in figure 10, comprise in jar portion 2 pressure from 1.5MPa become 2.5MPa during, acoustic pressure almost maintains certain level, the sort of acoustic pressure that therefore is difficult to produce silent mode is poor.Therefore, the operator is difficult to recognize noise when using air compressor 1, and the uncomfortable feeling that the driving acoustic conductance can be caused reduces to more than the sound pressure level of reality.
In addition, the rotating speed of driven motor part 3 is maintained necessarily at 1800rpm under silent mode in the past, relative therewith, after the pressure of rotating speed in jar portion 2 of driven motor part 3 under the super-silent pattern reaches 2.5MPa, reduce, therefore also can think and compare the silent mode degradation to 1500rpm.But, before pressure in jar portion 2 reached 1.5MPa, the rotating speed of motor part 3 maintained 1900rpm, therefore as a result of, even when air compressor 1 drives, also can keep performance equal when under silent mode, driving under super-silent pattern.
The compressor of the present invention that more than utilized description of drawings, but compressor of the present invention is not limited to the formation shown in the above-mentioned exemplary embodiments.Can be clear and definite, those skilled in the art can expect various modifications or modification in the category that the scope of patent application is put down in writing, these also belong to technical scope of the present invention certainly as can be known.
For example, in the air compressor 1 of exemplary embodiments, be illustrated for the situation of carrying out following control: in the microprocessor 25, before force value in jar portion 2 reaches 1.5MPa, the rotating speed of motor part 3 is maintained 1900rpm, force value in jar portion 2 from 1.5MPa to 2.5MPa during, the rotating speed of motor part 3 is reduced linearly, after force value in jar portion 2 becomes more than the 2.5MPa, the rotating speed of motor part 3 is maintained 1500rpm, but this setting example is an example, can also be respectively according to the capacity of jar portion 2, the variation characteristic of the cylinder load of first 13a of air compressing mechanism portion and second 13b of air compressing mechanism portion suitably changes to setting value respectively with the rotating speed of the motor part 3 of setting and the force value in the jar portion 2.
In addition, in the air compressor 1 of exemplary embodiments, variation by the piston load of the variation of the piston load of first 13a of air compressing mechanism portion and second 13b of air compressing mechanism portion, load value is consistent and jar portion 2 interior force value that can influence are 1.5MPa each other, therefore be the control that benchmark changes the rotating speed of motor part 3 as mentioned above with 1.5MPa, but the variation of the piston load of the first air compressing mechanism portion and the second air compressing mechanism portion is under the situation different with first 13a of air compressing mechanism portion of the air compressor 1 of exemplary embodiments and second 13b of air compressing mechanism portion, and also can make the force value as the jar portion of the benchmark of the rotating speed of change motor part is the value different with exemplary embodiments.
Claims (3)
1. compressor, rotation based on motor (3) drives the first pressurized air generating apparatus (13a) positioned opposite to each other and the second pressurized air generating apparatus (13b), generate pressurized air thus and be stored in the storage tank (8), in the described compressor (1), possess:
Control the rotation driven quantity control device (5) of the rotation driven quantity of described motor (3); And
Detect the pressure state detection unit (12) of the pressure state in the described storage tank (8),
The load that the load that the described first pressurized air generating apparatus (13a) is loaded and the described second pressurized air generating apparatus (13b) are loaded is according to the pressure state of described storage tank (8) and different,
When being in the predetermined range by the detected pressure state of described pressure state detection unit (12), the rotation driven quantity that described rotation driven quantity control device (5) makes described motor (3) is compared minimizing when outer with being in predetermined range,
Scope before and after the force value of the described storage tank (8) when the described predetermined range of the described pressure state load value that to be the described first pressurized air generating apparatus (13a) load value of being loaded loaded with the described second pressurized air generating apparatus (13b) is consistent.
2. compressor as claimed in claim 1, wherein,
The force value of the described storage tank (8) the when load value that the load value that the described first pressurized air generating apparatus (13a) is loaded and the described second pressurized air generating apparatus (13b) are loaded is consistent is the value of the central authorities of the CLV ceiling limit value of described predetermined range of described pressure state and lower limit.
3. compressor as claimed in claim 1 or 2, wherein,
The described rotation driven quantity of the described motor that reduces in described rotation driven quantity control device (5) is set to following degree: make the acoustic pressure of the driving sound of the compressor after carrying out this minimizings keep the acoustic pressure of the driving sound that reduces preceding compressor.
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| Application Number | Priority Date | Filing Date | Title |
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| JP2009-168795 | 2009-07-17 | ||
| JP2009168795A JP5163607B2 (en) | 2009-07-17 | 2009-07-17 | compressor |
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| CN101956696A true CN101956696A (en) | 2011-01-26 |
| CN101956696B CN101956696B (en) | 2014-07-30 |
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2506792Y (en) * | 2001-10-25 | 2002-08-21 | 骐成科技股份有限公司 | Air compressor with electricity management controller |
| CN2599280Y (en) * | 2002-10-25 | 2004-01-14 | 胡瑞华 | Fully automatic air compressor controller |
| CN2663688Y (en) * | 2003-11-28 | 2004-12-15 | 夏武 | Automatic control device of air compressor |
| JP2005090321A (en) * | 2003-09-16 | 2005-04-07 | Tetsuji Tatsuoka | Power generation device |
| JP4203292B2 (en) * | 2002-09-27 | 2008-12-24 | 株式会社日立製作所 | air compressor |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0693964A (en) * | 1992-09-09 | 1994-04-05 | Aisin Seiki Co Ltd | Plunger pump |
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Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2506792Y (en) * | 2001-10-25 | 2002-08-21 | 骐成科技股份有限公司 | Air compressor with electricity management controller |
| JP4203292B2 (en) * | 2002-09-27 | 2008-12-24 | 株式会社日立製作所 | air compressor |
| CN2599280Y (en) * | 2002-10-25 | 2004-01-14 | 胡瑞华 | Fully automatic air compressor controller |
| JP2005090321A (en) * | 2003-09-16 | 2005-04-07 | Tetsuji Tatsuoka | Power generation device |
| CN2663688Y (en) * | 2003-11-28 | 2004-12-15 | 夏武 | Automatic control device of air compressor |
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| JP5163607B2 (en) | 2013-03-13 |
| JP2011021569A (en) | 2011-02-03 |
| CN101956696B (en) | 2014-07-30 |
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