CN101956696B - Compressor - Google Patents
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- CN101956696B CN101956696B CN201010230170.0A CN201010230170A CN101956696B CN 101956696 B CN101956696 B CN 101956696B CN 201010230170 A CN201010230170 A CN 201010230170A CN 101956696 B CN101956696 B CN 101956696B
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Abstract
In a compressor (1), a first compressed air generating device (13a) and a second compressed air generating device (13b) which are oppositely arranged are driven by rotating a motor (3) so as to generate compressed air and store in a storage jar (8). The compressor (1) is provided with a rotation driving volume control part (5) for controlling the rotation driving volume of the motor (3) and a pressure state detecting part (12) for detecting the pressure state in the storage jar (8). The loads borne by the first and second compressed air generating devices (13a) and (13b) are variable according to the pressure state of the storage jar (8). When the pressure state detected by the pressure state detecting part (12) is in a specialized range rather than out of the specialized range, the rotation driving volume control part (5) reduces the rotation driving volume of the motor (3). The specialized range of the pressure state is the range of the pressure value before and after the pressure value of the storage jar (8) when the loads borne by the first and second compressed air generating devices (13a) and (13b) are accordant.
Description
Technical field
The present invention relates to compressor, more specifically, relate to following compressor: the rotary actuation based on motor drives the first pressurized air generating apparatus positioned opposite to each other and the second pressurized air generating apparatus, generates thus pressurized air, and is stored in storage tank.
Background technique
Use the driving tool of utilizing compressed-air actuated nailing maching etc. in building site, for driving tool is supplied with to pressurized air, air compressor need to be set.Air compressor is following structure: by drive motor portion, utilize pressurized air generating unit to generate pressurized air, the pressurized air of generation is stored in to tank portion, supply with pressurized air thus to driving tool.
The in the situation that of using driving tool at this compressor of application, there is the tendency that produces noise (driving sound) in the time of the driving of compressor.Therefore, there is following compressor: consider the situation of carrying out operation operators such as nights to possess the operation mode (for example, with reference to patent documentation 1) of " silent mode " in order to reduce driving sound.
Patent documentation 1:JP-B2-4203292
In the compressor that possesses silent mode, reduce compared with the rotating speed of the rotating speed that makes motor during with common running and maintain certain rotating speed, realize thus the reduction of driving sound.
But in the compressor recently utilizing, in order to use multiple driving tool simultaneously, or consideration utilizes the use of the driving tool of elevated pressures, the tendency that existence maintains the pressure state in tank high pressure and further makes tankage size maximize.Like this pressure in tank being maintained in the compressor of high pressure, exist driving sound to become large tendency, require further to reduce driving sound.In addition, as mentioned above, in the compressor maximizing at tankage size, if carry out as object the control that the rotating speed of motor is limited lowlyer to reduce driving sound, sometimes follow the reduction of rotating speed and the performance of compressor is reduced.
Summary of the invention
More than one embodiment of the present invention, provides a kind of compressor, and it can maintain with more than silent mode equal extent in the past performance and compared 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 rotary actuation 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 thus pressurized air, and be stored in storage tank 8, compressor 1 possesses the rotary actuation amount control device 5 of the rotary actuation amount of controlling described motor 3 and detects the pressure state detection unit 12 of the pressure state in described storage tank 8.The load that the load that described the first pressurized air generating apparatus 13a loads and described the second pressurized air generating apparatus 13b load is according to the pressure state of described storage tank 8 and difference.In the time that the pressure state being detected by described pressure state detection unit 12 is in predetermined range, described rotary actuation amount control device 5 makes the minimizing compared with in outside predetermined range time of the rotary actuation amount of described motor 3.The described predetermined range of described pressure state is the scope before and after the force value of the described storage tank 8 of load value that described the first pressurized air generating apparatus 13a the loads load value of loading with described the second pressurized air generating apparatus 13b when consistent.The rotary actuation amount of the motor reducing in addition, in predetermined range time is not zero.In addition, in the described predetermined range of described force value, do not comprise zero.
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 loaded separately with the second pressurized air generating apparatus 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 effectively accumulated the pressurized air of authorized pressure 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 mostly adopting in general compressor.
In the compressor of this structure, usually, the first pressurized air generating apparatus and the second pressurized air generating apparatus relatively arrange, when the load value of therefore loading with the second pressurized air generating apparatus at the load value that the first pressurized air generating apparatus is loaded 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 rotary actuation amount control device of the compressor of embodiments of the invention, obtain in advance the pressure state of load value that load value that the first pressurized air generating apparatus loads loads with the second pressurized air generating apparatus storage tank when consistent, when pressure state in the time that the pressure state being detected by pressure state detection unit is consistent with the aforesaid load value of obtaining in advance approaches (, in the front and back scope of the pressure state when consistent), make energetically the rotary actuation amount (compared with scope in addition) of motor reduce.Consequently, can suppress the increase of the acoustic pressure of the driving sound of the compressor that rotary actuation, the compression movement of the first pressurized air generating apparatus and the compression movement of the second pressurized air generating apparatus etc. of motor cause.
In addition, the described rotary actuation amount of the described motor reducing in described rotary actuation amount control device can be also the rotary actuation amount that is set as following degree: make the acoustic pressure of the driving sound that carries out the compressor after this minimizing maintain the acoustic pressure of the driving sound of the compressor before reducing.
Like this, so that carry out the acoustic pressure of the driving sound of the compressor after the minimizing of motor rotary actuation amount and maintain the degree of the acoustic pressure of the driving sound of the compressor before the minimizing of carrying out motor rotary actuation amount, the rotary actuation amount of motor is reduced, the driving sound that load value that load value that the first pressurized air generating apparatus loads loads with the second pressurized air generating apparatus can rise when consistent not only can be reduced energetically thus, the sound pressure variations of the driving sound before and after the rotary actuation amount that reduces motor can also be made operator wait to be difficult to recognize.Therefore, can reduce operator recognizes and the situation of driving sound can suppress to hear that the operator of driving sound feels noisy situation because of sound pressure variations etc.
In the rotary actuation amount control device of the compressor of embodiments of the invention, in the predetermined range of the front and back of the pressure state of storage tank when load value that the load value of loading in the first pressurized air generating apparatus at the pressure state being detected by pressure state detection unit is loaded with the second pressurized air generating apparatus is consistent time, reduce energetically the rotary actuation amount of motor, can suppress thus the increase of the acoustic pressure of the driving sound of compressor.
Brief description of the drawings
Fig. 1 is the block diagram that represents the summary formation of the air compressor of exemplary embodiments.
Fig. 2 is the sectional drawing that represents the air compressing mechanism portion of exemplary embodiments and the formation of motor part.
Fig. 3 is the figure that changes the load value variation that represents the piston load relevant with the first air compressing mechanism portion of exemplary embodiments and the second air compressing mechanism portion according to pressure in tank portion.
Fig. 4 is the block diagram that represents the control circuit portion of the air compressor of exemplary embodiments.
Fig. 5 is the acoustic pressure of the driving sound of the air compressor while representing that according to the force value of tank portion the rotating speed of the motor part of exemplary embodiments is 1000rpm～1800rpm, the figure of the variation of the acoustic pressure of the driving sound of air compressor while motor part being driven with the rotating speed used with normal mode.
Fig. 6 is the figure of the variation of the acoustic pressure of the driving sound of the air compressor while representing that according to the force value of tank portion the rotating speed of the motor part of exemplary embodiments is 1500rpm, 1800rpm～2200rpm.
Fig. 7 is the flow chart that represents the processing of the microprocessor of the control circuit portion of exemplary embodiments.
The situation that Fig. 8 is the situation that is 2.0MPa of the design of pressure in the tank portion to the rotating speed of motor part being reached to 1500rpm in the air compressor of exemplary embodiments, be set as the situation of 2.25MPa and be set as 2.5MPa compares the figure of the state of changing that represents driving sound.
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 tank portion.
Figure 10 is the figure that represents the acoustic pressure of 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 tank portion.
Embodiment
Below, as an example of compressor of the present invention, utilize accompanying drawing at length to describe air compressor.
Fig. 1 is the block diagram that represents the summary formation of the air compressor of exemplary embodiments.Air compressor 1 is roughly made up of tank 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 (rotary actuation amount control device) 5.
Tank portion 2 has for storing compressed-air actuated storage tank 8.In storage tank 8, store the pressurized air of the certain pressure being generated by pressurized air generating unit 4, conventionally maintain the pressure of 3.5MPa～4.3MPa degree.
Be provided with multiple pressurized air conveying ends 9 at storage tank 8.In the air compressor 1 of exemplary embodiments, be provided with compressed-air actuated high pressure conveying end 9a for taking out high pressure and for taking out the compressed-air actuated normal pressure conveying end 9b of normal pressure, at high pressure conveying end 9a, the compressed-air actuated pressure being 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 being taken out by reduction valve 10b is decompressed to 0.7MPa～1.5MPa degree.In addition,, in order to be supplied with to driving tool such as nailing machings by the pressurized air of reduction valve 10a, 10b decompression, can set up, unload steam hose (diagram is omitted) at each conveying end 9a, 9b.
In addition, in storage tank 8, be provided with the pressure transducer (pressure state detection unit) 12 for detection of the pressure in storage tank 8.Pressure transducer 12 has the function that by inner pressure cell, the pressure variation in storage tank 8 is converted to electrical signal, and the electrical signal detecting is passed to control circuit portion 5.
Motor part 3 has the effect of the driving force that produces the reciprocating motion of the pistons for making pressurized air generating unit 4.In motor part 3, be provided with stator 16 and rotor 17 for generation of driving force.On stator 16, be formed with the coil of U phase, V phase, W phase, for these coil current flowings, form thus rotating magnetic field.Rotor 17 is made up of permanent magnet, the rotating magnetic field forming by the electric current of the coil because flowing through stator 16, and rotor 17 rotates.
Pressurized air generating unit 4 is following structure: have the air compressing mechanism portion 13 being roughly made up of piston and cylinder, make the reciprocating motion of the pistons that arranges in cylinder, will be incorporated into the air compressing in cylinder from the Aspirating valves of cylinder, thereby generate pressurized air.
In general pressurized air generating unit (comprising the pressurized air generating unit 4 of exemplary embodiments), as shown in Figure 2, be provided with two air compressing mechanism portions 13 that roughly formed by piston and cylinder.The 13a of the first air compressing mechanism portion (the first pressurized air generating apparatus) that forms 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 forms by cylinder bore, and the 13b of the second air compressing mechanism portion (the second pressurized air generating apparatus) that forms 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 forms by cylinder bore.
In addition, motor part 3 is setting adjacent with pressurized air generating unit 4 as shown in Figure 2, the structure that while rotation as mentioned above for the rotor 17 of motor part 3, the running shaft 19 of motor part 3 is rotated.It is rotatably mounted that the running shaft 19 of motor part 3 is rotated axle bearing 20a, 20b, on running shaft 19, be linked with the connecting rod 21a of first piston 15a via bearing portion (crank bearing) 22a, in addition, the connecting rod 21b of the second piston 15b is linked on running shaft 19 via bearing portion (crank bearing) 22b.And, on the end of running shaft 19, be provided with the fan 23 for importing extraneous gas.
When the running shaft 19 of motor part 3 starts to rotate, the first piston 15a of the first 13a of air compressing mechanism portion is accompanied by the advance and retreat mobile (piston movement) 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 the second 13b of air compressing mechanism portion is accompanied by the advance and retreat mobile (piston movement) 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 the first 13a of air compressing mechanism portion is 60mm, stroke is defined as 25mm, on the other hand, the first piston 15a cylinder bore of the second 13b of air compressing mechanism portion is 40mm, stroke is defined as 10mm, in the first 13a of air compressing mechanism portion the pressure state of compressed air and in the 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 the first 13a of air compressing mechanism portion by after air compressing, further utilize the second 13b of air compressing mechanism portion to be formed as the compression processing of high pressure to compressed air in the first 13a of air compressing mechanism portion, can effectively carry out thus the pressure control in tank portion 2.
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 respectively first piston 15a and the second piston 15b is also different values.Fig. 3 changes and represents that the load value of the piston load relevant with the second 13b of air compressing mechanism portion with the first 13a of air compressing mechanism portion changes the figure of (load value state of changing) according to the pressure in tank portion 2.
As shown in Figure 3, for example, when force value in storage tank 8 is lower (0MPa～0.6MPa degree), the first 13a of air compressing mechanism portion is applied positive load and makes the pressure rise in tank portion 2, but the load that puts on the first 13a of air compressing mechanism portion becomes in predetermined value (being about 160kgf degree in exemplary embodiments) state culminating because of the ability of the first 13a of air compressing mechanism portion.
The load of the first 13a of air compressing mechanism portion reaches after predetermined value, utilizes the second 13b of air compressing mechanism portion to compress compressed air in the first 13a of air compressing mechanism portion, improves thus the pressure in tank portion 2.Therefore, the load that puts on the second 13b of air compressing mechanism portion increases lentamente compared with the first 13a of air compressing mechanism portion, the predetermined value (about 160kgf) that exceedes the first 13a of air compressing mechanism portion, rises pro rata with the pressure rise in tank portion 2.
In the second 13b of air compressing mechanism portion, compressed air is supplied with to the storage tank 8 of tank portion 2 via connecting pipe 14 (with reference to Fig. 1).
Control circuit portion 5 as shown in Figure 4, is roughly made up of microprocessor (MPU:Micro ProcessingUnit) 25, converter circuit 26, converter circuit 27.
Converter circuit 26 is roughly made up of rectification circuit 28, booster circuit 29 and smoothing circuit 30, carries out so-called PAM control by this converter circuit 26.Herein, so-called PAM controls and refers to that the height by utilizing converter circuit 26 to change the pulse of output voltage controls the method for the rotating speed of motor part 3.On the other hand, in converter circuit 27, carrying out so-called PWM controls.So-called PWM controls and refers to that the pulse width that changes output voltage controls the method for the rotating speed of motor part 3.Microprocessor 25, according to the operating condition of air compressor 1, suitably switches PWM control and execution control that the PAM being undertaken by converter circuit 26 controls and undertaken by converter circuit 27.
The rectification circuit 28 of converter circuit 26 and smoothing circuit 30 have by the ac power supply 31 of the driving source to as air compressor 1 and carry out rectification/smoothly convert to the function of VDC.Be provided with switching element 29a in the inside of booster circuit 29, there is 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.
Converter circuit 27 has following function: the pulse of the VDC of being changed by converter circuit 26 is carried out to positive and negative conversion with some cycles, and by commutation pulse width, VDC is converted to and has approximate sinusoidal wave alternating voltage.By adjusting this pulse width, can carry out as mentioned above the rotating speed control of motor part 3.The adjustment that microprocessor 25 carries out for the output value of converter circuit 27, controls the drive volume of motor part 3 thus.
Microprocessor 25 is the control units for control the compressed-air actuated pressure stability that makes tank portion 2 by the driving of carrying out converter circuit 26 and converter circuit 27.Microprocessor 25 be by the LSI of 1 realize operation processing unit (CPU:Central Processing Unit), the parts of the function of the RAM (Random AccessMemory), the ROM (Read Only Memory) that stores (programs of the contents processing shown in Fig. 7 etc.) such as control processors described later etc. that are utilized as the temporary storage area of operational store etc.
Input the force value information detecting in the pressure transducer 12 of tank portion 2 to microprocessor 25.In addition, microprocessor 25 is to export the formation of control information (PAM instruction, PWM instruction) to converter circuit 26 and converter circuit 27.
In converter circuit 26 and converter circuit 27, the control information based on being exported by microprocessor 25 carrys out the driving of operating motor portion 3 and controls.Particularly, microprocessor 25, by exporting PAM instruction to boost pressure controller 32, is controlled the switching element 29a of booster circuit 29 via boost pressure controller 32, carry out the driving control of converter circuit 26.In addition, similarly, microprocessor 25 is exported PWM instruction to converter circuit 27, carries out thus the control of converter circuit 27.
Then, describe for the sound pressure variations of the driving sound of the air compressor 1 of obtaining according to the rotating speed of motor part 3.
Fig. 5 be the air compressor 1 while representing that according to the force value of tank portion 2 rotating speed of motor part 3 is 1000rpm, 1100rpm, 1200rpm, 1300rpm, 1400rpm, 1500rpm, 1600rpm, 1700rpm and 1800rpm driving sound acoustic pressure and use with normal mode rotating speed drive motor portion 3 time the figure of variation of acoustic pressure of driving sound of air compressor 1.
In addition, the state that the rotating speed of motor part 3 is maintained to 1800rpm is equivalent to the drive condition under the silent mode of air compressor 1.In addition, Fig. 5 be illustrated in by driving voltage set/maintain the state of 100V, carry out in the position of fan 23 sides of motor part 3 driving sound acoustic pressure measure time data.
As shown in Figure 5, during with every speed drive motor portion 3 from 1000rpm to 1800rpm, during with drive motor portion 3 under normal mode compared with, acoustic pressure reduces.In addition,, during the force value in tank portion 2 reaches before 1.5MPa degree, under the whole rotating speed from 1000rpm to 1800rpm, the sound pressure variations of driving sound becomes mitigation (changing less state).
But, when force value in tank portion 2 is increased to 2.5MPa from 1.5MPa, in the situation that speed setting is 1600rpm～1800rpm, compared with the acoustic pressure increase of the driving sound of (before reaching 1.5MPa degree) is inclined to before this, acoustic pressure rises sharp.And the force value in tank portion 2, near exceeding 2.5MPa, in the motor part 3 that is 1600rpm～1800rpm, shows the tendency that acoustic pressure maintains or reduce a little at speed setting.
On the other hand, being below 1500rpm time by speed setting, as shown in Figure 5, show with tank portion 2 in force value (under the situation from 1.5MPa to 2.5MPa, be also) independently the tendency that the acoustic pressure of driving sound increases lentamente, be not absorbed in as by speed setting being the situation that 1600rpm drives the acoustic pressure of sound to rise sharp when above.
Therefore, can say, even using silent mode (rotating speed of motor part 3 is about 1800rpm) in the past also to have in the scope of the force value more than 1.5MPa that driving sound becomes large tendency, making the rotation of motor part 3 be reduced to the rotating speed of the rising that does not produce the sound of driving sharply, is effective for the acoustic pressure that reduces driving sound.Particularly, can judge as follows: as shown in Figure 5, do not produce driving sound sharply rising rotating speed and show therein the 1500rpm of the highest rotating speed before, the rotating speed of motor part 3 is reduced, thereby can realize the acoustic pressure that reduces driving sound.
In addition, the force value in tank portion 2 become 1.5MPa before during, under the whole rotating speed from 1000rpm to 1700rpm, demonstrate force value in driving sound and tank portion 2 tendency proportional and that increase lentamente.If consider this increase slowly,, by being the rotating speed higher than 1500rpm by the speed setting of motor part 3, even the variation of the force value in tank portion 2, the acoustic pressure variation that is also difficult to produce driving sound, can reduce driving sound variation acoustically.
Fig. 6 is the figure of the variation of the acoustic pressure of the driving sound of the air compressor 1 while representing that according to the force value of tank 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, be illustrated in by driving voltage set/maintain the state of 100V, carry out in the position of fan 23 sides of motor part 3 driving sound acoustic pressure measure time data.
Known according to Fig. 6, having set respectively in the motor part 3 of the rotating speed from 1800rpm to 2200rpm, identical with Fig. 5, force value in tank portion 2 is increased to the situation of 2.5MPa from 1.5MPa, compared with the increase tendency of the acoustic pressure of (below 1.5MPa degree) before this, show the tendency that acoustic pressure rises sharp.In addition, as shown in Figure 6, in the motor part 3 that is 1500rpm at rotating speed, compared with more than 1800rpm motor part 3, maintain the state that the acoustic pressure of driving sound reduces relatively.
On the other hand, the force value in tank portion 2 reach 1.5MPa before during, the acoustic pressure that is set as each motor part 3 of the rotating speed of 1500rpm, 1800rpm, 1900rpm demonstrate closer like sound pressure level.Therefore, the force value in tank portion 2 reach 1.5MPa before during, even the rotating speed 1800rpm of the motor part under silent mode 3 is reduced to 1500rpm etc., can not obtain energetically the effect that acoustic pressure reduces, on the contrary, though rise of rotational speed to 1900rpm, driving sound also can not enlarge markedly.
Especially, the acoustic pressure of the driving sound of the air compressor 1 during before reaching 1.5MPa for the force value in tank portion 2, being preferably maintained with the force value in tank portion 2 is the degree that the acoustic pressure of driving sound of the air compressor 1 of 2.5MPa while the speed setting of motor part 3 being 1500rpm when above is identical.Like this, the acoustic pressure that is the driving sound of 2.5MPa when above by the force value in acoustic pressure and the tank portion 2 of the driving sound during the force value in tank portion 2 being reached before 1.5MPa maintains same degree, can make thus operator's grade be difficult to the sound pressure variations of the driving sound of the front and back of the rotary actuation amount of recognizing reduction motor part.Therefore, can reduce operator recognizes and the situation of driving sound can suppress to hear that the operator of driving sound feels noisy situation because of sound pressure variations etc.
Consider these aspects, consider in addition that the performance of tank portion 2 maintains/improve, can judge: while determining the rotating speed of the motor part 3 during force value in tank portion 2 reaches before 1.5MPa, be preferably 1900rpm by speed setting.
Like this, in the air compressor 1 of exemplary embodiments, when the rotating speed of each motor part 3 is asked for to the driving sound state of the air compressor 1 changing according to the force value of tank portion 2, there is the tendency of interior pressure temporary transient increase from about 1.5MPa to about 2.5MPa of tank portion 2.As its reason, can think because toward each other and the compression movement of the compression movement of horizontally disposed the first 13a of air compressing mechanism portion and the second 13b of air compressing mechanism portion influences each other and produces vibration etc.
General compressor possesses the air compressing mechanism portion of two cylinders that level as described above relatively configures.These two air compressing mechanism portions are in order effectively to reduce respectively the pressure in tank portion 2, in a side air compressing mechanism portion by the pressure decreased of extraneous gas to certain value, then, in the opposing party's air compressing mechanism portion, the air of the air compressing mechanism portion compression by a side is further compressed, thus the pressure in tank portion 2 is brought up to the force value of expectation and maintained.
In the air compressor 1 of exemplary embodiments, carry out at first first 13a of air compressing mechanism portion of compression of extraneous gas with compared with the second 13b of air compressing mechanism portion that further compress processing by the air of the first 13a of air compressing mechanism portion compression, cylinder bore and stroke amount are larger, for the first 13a of air compressing mechanism portion and the 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, in the case of making the pressure rise in tank portion 2, the load value of the piston load of the first 13a of air compressing mechanism portion changes and the load value of the piston load of the second 13b of air compressing mechanism portion change distinguish different.If note the load value of the piston load of each air compressing mechanism portion, in first 13a of air compressing mechanism portion and the second 13b of air compressing mechanism portion of the air compressor 1 of exemplary embodiments, comparing the second 13b of air compressing mechanism portion at the load value of air compressor 1 firm piston load of starting rear the first 13a of air compressing mechanism portion rises sharp, when interior pressure in tank portion 2 reaches 0.6MPa, load value reaches about 160kgf and becomes the state (maintaining the state of about 160kgf) culminating.
On the other hand, about the second 13b of air compressing mechanism portion, the load value of piston load is compared the rising of the load value of the first 13a of air compressing mechanism portion and is risen lentamente.The second 13b of air compressing mechanism portion of the air compressor 1 of exemplary embodiments demonstrates according to the pressure rise in tank portion 2 and the tendency of piston load rising.According to the difference of the load value rising characteristic of the load value rising characteristic of this first air compressing mechanism 13a of portion (load value state of changing) and the second 13b of air compressing mechanism portion, in air compressor 1, in the time that air compressor 1 starts, carry out rapidly the compression processing of the first 13a of air compressing mechanism portion, in in tank portion 2, press under the state rising to a certain degree, make compression process main body shift to the second 13b of air compressing mechanism portion from the first 13a of air compressing mechanism portion, successfully carry out thus in tank portion 2 thereafter in press liter.
In the variation of the piston load of this first air compressing mechanism 13a of portion and the second 13b of air compressing mechanism portion, the force value of the tank portion 2 when each load value is consistent is 1.5MPa in the air compressor 1 of exemplary embodiments, the prespecified range of for example, force value in the tank portion 2 that the acoustic pressure that the value (1.0MPa～2.0MPa) of the front and back of this force value is equivalent to motor part 3 starts to rise.
Can be judged as this be because: under the first 13a of air compressing mechanism portion state consistent with the load value of the piston load of the second 13b of air compressing mechanism portion, the piston movement of the piston movement of the first 13a of air compressing mechanism portion and the second 13b of air compressing mechanism portion interacts, the impact in the gap of bearing, the support material etc. of supporting motor portion 3, the first 13a of air compressing mechanism portion and the second 13b of air compressing mechanism portion becomes maximum, and it is large that vibration etc. become.Therefore, can be judged as in the force value in the producible tank of the impact bringing at this piston movement portion 2, exist the driving of air compressor 1 to state tendency clear.
Therefore, in the air compressor 1 of exemplary embodiments, in control circuit portion 5, obtain in advance the interior pressure in the tank portion 2 that the piston load of the first 13a of air compressing mechanism portion is consistent with the piston load of the second 13b of air compressing mechanism portion, based on the force value of this tank portion 2, change the control of the rotation status of motor part 3, realize thus the processing of the driving sound that reduces air compressor 1.
Fig. 7 is the flow chart that represents the processing of the microprocessor 25 of control circuit portion 5.Microprocessor 25 is according to the control program of the middle storages such as ROM, the processing of the flow chart shown in execution graph 7.
First microprocessor 25 is 1900rpm (step S.1) by the speed setting of motor part 3, so that the mode that rotor 17 rotates with the rotating speed of having set is carried out the driving control (step S.2) of motor part 3.Particularly, microprocessor 25 for example, in order to make the rotation of rotor 17 of motor part 3 become the rotating speed (1900rpm) of setting, export PAM instruction to boost pressure controller 32, export PWM instruction to converter circuit 27, the rotation status of the rotor of motor part 3 17 is controlled to 1900rpm.
Then, microprocessor 25 is obtained the force value (step S.3) in tank portion 2 via pressure transducer 12.Then, microprocessor 25 judges whether the force value in tank portion 2 is the value (step S.4) that is greater than 1.5MPa.Force value in tank portion 2 be not while being greater than the value of 1.5MPa (more than 0Pa and below 1.5MPa time, step S.4 in during for "No"), the rotating speed of motor part 3 is maintained 1900rpm (step S.1) by microprocessor 25, carry out the driving control (step S.2) of motor part 3, again obtain the force value (step S.3) in tank portion 2, judge whether the force value in tank portion 2 is the value (step S.4) that is greater than 1.5MPa.
Force value in tank portion 2 is (step S.4 in for "Yes" time) while being greater than the value of 1.5MPa, and microprocessor 25 judges whether the force value in tank portion 2 is the value (step S.5) that is less than 2.5MPa.Force value in tank portion 2 be not while being less than the value of 2.5MPa (when 2.5MPa is above, step S.5 in during for "No"), microprocessor 25 is 1500rpm (step is S.6) by the speed setting of motor part 3.Then, microprocessor 25 is so that the mode that the rotating speed of motor part 3 is 1500rpm is carried out the driving control (step S.2) of motor part 3.Then, microprocessor 25 is described above, obtains the force value (step S.3) in tank portion 2, repeats the judgement (step S.4) whether force value in tank portion 2 is greater than the value of 1.5MPa.
On the other hand, force value in tank portion 2 be while being less than the value of 2.5MPa (force value in tank portion 2 is when being greater than the value of 1.5MPa and being less than the value of 2.5MPa, step S.5 in during for "Yes"), microprocessor 25 is according to the rotating speed of the design of pressure motor part 3 in tank portion 2 (step is S.7).
Particularly, microprocessor 25 is set the rotating speed of motor part 3 in the following manner: when the force value in tank portion 2 is 1.5MPa, the rotating speed that makes motor part 3 is 1900rpm, then along with the force value in tank portion 2 rises and make linearly the rotating speed of motor part 3 reduce, when force value in tank portion 2 reaches 2.5MPa, the rotating speed that makes motor part 3 is 1500rpm., in the air compressor 1 of exemplary embodiments, be, the formation that the rotating speed of motor part 3 is reduced linearly according to the interior pressure in tank portion 2.The rotating speed of the motor part 3 corresponding with force value in tank portion 2 can be to be stored in the data in the ROM etc. of microprocessor 25 as table data in advance, in addition, can be also the data that microprocessor 25 calculates according to the force value in tank portion 2.
In addition, in the air compressor 1 of exemplary embodiments, adopt following method: when the force value in tank portion 2 is 1.5MPa, being 1900rpm by the speed setting of motor part 3, when the force value in tank portion 2 is 2.5MPa, is 1500rpm by the speed setting of motor part 3, determine linearly thus the rotating speed of motor part 3, but the force value speed setting of motor part 3 being changed in the tank portion 2 of 1500rpm is not necessarily limited to 2.5MPa, can be also 2.0MPa, can also be 2.25MPa.Force value in this tank portion 2 can suitably change by cylinder bore, the stroke amount of the first 13a of air compressing mechanism portion and the second 13b of air compressing mechanism portion.
The situation that Fig. 8 is the situation that is 2.0MPa of the design of pressure in the tank portion 2 to the rotating speed of motor part 3 being reached to 1500rpm in the air compressor 1 of exemplary embodiments, be set as the situation of 2.25MPa and be set as 2.5MPa compares the figure of the state of changing that represents driving sound.In addition, Fig. 8 is the coordinate diagram that is illustrated in the value of the acoustic pressure of the motor part 3 in the processing that fan 23 sides are determined at tank portion 2 interior using charged air pressures.
In the air compressor 1 of exemplary embodiments, as shown in Figure 8, the sound pressure variations minimum of driving sound when design of pressure in tank portion 2 is 2.5MPa, the design of pressure in the tank portion 2 while therefore the rotating speed of motor part 3 being reduced to 1500rpm is 2.5MPa, to realize the variation that reduces driving sound.In addition, in the air compressor 1 of exemplary embodiments, the sound pressure variations minimum of driving sound when design of pressure in tank portion 2 is 2.5MPa, but not 2.5MPa always of force value in the tank portion 2 of the sound pressure variations minimum of driving sound, the force value of therefore setting is not limited to 2.5MPa.
As mentioned above, microprocessor 25, according to after the rotating speed of the design of pressure motor part 3 in tank portion 2 (rotating speed of rotor 17) (step S.7), carries out the driving control (step S.2) of motor part 3 in rotating speed rotary driving motor portion 3 modes according to having set.After, microprocessor 25, by repeating above-mentioned contents processing, changes the setting of the rotating speed of motor part 3 according to the force value in tank portion 2, carry out the driving control of air compressor 1.
Fig. 9 is the coordinate diagram that represents the rotating speed of the motor part 3 in the super-silent pattern that proposes in the common operation mode of air compressor 1, the in the past silent mode that uses and exemplary embodiments according to the force value in tank portion 2, and Figure 10 is the coordinate diagram that represents the acoustic pressure of the driving sound of the air compressor 1 in above-mentioned three patterns according to the force value in tank 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 tank portion 2, but for this rotation speed change, microprocessor 25 is not to control according to the force value in tank portion 2, but according to the rotating speed of the power value control motor part 3 of ac power supply 31, therefore can not carry out energetically the control of the force value based in tank portion 2.Under common operation mode, in order to improve as soon as possible the force value in tank portion 2 when the starting of air compressor 1, consider power value tolerance and slightly highland set the control of the rotating speed of motor part 3.Therefore, there is no actively to consider the acoustic pressure of reduction motor part 3.
Under silent mode, because the driving sound to reduce air compressor 1 is as first object, therefore regardless of the force value in tank portion 2, the rotating speed of motor part 3 is set in to 1800rpm all the time and turns round.On the other hand, under the super-silent pattern proposing in exemplary embodiments, to 1.5MPa, be 1900rpm by the speed setting of motor part 3, between 1.5MPa～2.5MPa, the rotating speed of motor part 3 is reduced linearly, is that 1500rpm turns round by the speed setting of motor part 3 after 2.5MPa.
Under three each operation modes, the driving sound while running if will set as mentioned above the rotating speed of motor part 3 compares like this, and as shown in figure 10, the driving sound while driving under normal mode demonstrates peak.On the other hand, while driving under silent mode driving sound when driving under normal mode compared with acoustic pressure reduce, but the pressure in tank portion 2 becomes acoustic pressure between 2.5MPa from 1.5MPa and rises sharp, therefore worry that operator can be appreciated that the noise of air compressor 1 and feels noisy because the force value in tank portion 2 is that force value in driving sound and the tank portion 2 producing below 1.5MPa time is that acoustic pressure between the driving sound of 2.5MPa generation when above is poor etc.
But under super-silent pattern, as shown in figure 10, the pressure in tank portion 2 becomes during 2.5MPa from 1.5MPa, acoustic pressure almost maintains certain level, that acoustic pressure that is therefore difficult to produce silent mode is poor.Therefore, operator is difficult to recognize noise when air compressor 1 using, more than the uncomfortable feeling that drives acoustic conductance cause can being reduced to actual sound pressure level.
In addition, under silent mode in the past, the rotating speed of driven motor part 3 is maintained necessarily at 1800rpm, on the other hand, under super-silent pattern the pressure of the rotating speed of driven motor part 3 in tank portion 2 reach 2.5MPa with rear to 1500rpm reduce, therefore also can think and compare silent mode degradation.But, before pressure in tank portion 2 reaches 1.5MPa, the rotating speed of motor part 3 maintains 1900rpm, therefore as a result of, even when air compressor 1 drives under super-silent pattern, also can maintain performance equal when driving under silent mode.
The compressor of the present invention that more than utilized brief description of the drawings, but compressor of the present invention is not limited to the formation shown in above-mentioned exemplary embodiments.Can be clear and definite, in the category that those skilled in the art record in the scope of patent application, can expect various modifications or modification, known these also belong to technical scope of the present invention certainly.
For example, in the air compressor 1 of exemplary embodiments, be illustrated for the situation of carrying out following control: in microprocessor 25, before force value in tank portion 2 reaches 1.5MPa, the rotating speed of motor part 3 is maintained to 1900rpm, force value in tank portion 2 from 1.5MPa to 2.5MPa during, the rotating speed of motor part 3 is reduced linearly, after force value in tank portion 2 becomes more than 2.5MPa, the rotating speed of motor part 3 is maintained to 1500rpm, but this setting example is an example, can also be respectively according to the capacity of tank portion 2, the force value in the rotating speed of the motor part of setting 3 and tank portion 2 is suitably changed to respectively setting value by the variation characteristic of the cylinder load of the first 13a of air compressing mechanism portion and the second 13b of air compressing mechanism portion.
In addition, in the air compressor 1 of exemplary embodiments, by the variation of piston load of the first 13a of air compressing mechanism portion and the variation of the piston load of the second 13b of air compressing mechanism portion, force value in the tank portion 2 that load value unanimously can affect is each other 1.5MPa, the control of therefore changing the rotating speed of motor part 3 taking 1.5MPa as benchmark as mentioned above, but the variation of the piston load of the first air compressing mechanism portion and the second air compressing mechanism portion is in the case of different from the first 13a of air compressing mechanism portion of the air compressor 1 of exemplary embodiments and the second 13b of air compressing mechanism portion, also can make as the force value of tank portion of benchmark of the rotating speed that changes motor part is the value different from exemplary embodiments.
Claims (2)
1. a compressor, rotary actuation 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 storage tank (8), in described compressor (1), possessing:
Control the rotary actuation amount control device (5) of the rotary actuation amount of described motor (3); And
Detect the pressure state detection unit (12) of the pressure state in described storage tank (8),
The load that the load that described the first pressurized air generating apparatus (13a) is loaded is loaded from described the second pressurized air generating apparatus (13b) is according to the pressure state of described storage tank (8) and different,
In the time that the pressure state being detected by described pressure state detection unit (12) is in predetermined range, described rotary actuation amount control device (5) makes the minimizing compared with in outside predetermined range time of the rotary actuation amount of described motor (3),
The described predetermined range of described pressure state is the scope before and after the force value of the described storage tank (8) of load value that described the first pressurized air generating apparatus (13a) the is loaded load value of loading with described the second pressurized air generating apparatus (13b) when consistent
The force value of the described storage tank (8) when load value that the load value that described the first pressurized air generating apparatus (13a) is loaded is loaded with described the second pressurized air generating apparatus (13b) is consistent is the CLV ceiling limit value of described predetermined range and the central value of lower limit of described pressure state.
2. compressor as claimed in claim 1, wherein,
The described rotary actuation amount of the described motor reducing in described rotary actuation amount control device (5) is set to following degree: make the acoustic pressure of the driving sound that carries out the compressor after this minimizing maintain the acoustic pressure of the driving sound of the compressor before reducing.
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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 CN101956696A (en) | 2011-01-26 |
| CN101956696B true CN101956696B (en) | 2014-07-30 |
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Citations (4)
| 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 |
| JP4203292B2 (en) * | 2002-09-27 | 2008-12-24 | 株式会社日立製作所 | air compressor |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0693964A (en) * | 1992-09-09 | 1994-04-05 | Aisin Seiki Co Ltd | Plunger pump |
| JP2005090321A (en) * | 2003-09-16 | 2005-04-07 | Tetsuji Tatsuoka | Power generation device |
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2009
- 2009-07-17 JP JP2009168795A patent/JP5163607B2/en active Active
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Patent Citations (4)
| 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 |
| CN2663688Y (en) * | 2003-11-28 | 2004-12-15 | 夏武 | Automatic control device of air compressor |
Non-Patent Citations (2)
| Title |
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| JP特开2005-90321A 2005.04.07 |
| JP特许第4203292号B2 2008.12.24 |
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| JP2011021569A (en) | 2011-02-03 |
| CN101956696A (en) | 2011-01-26 |
| JP5163607B2 (en) | 2013-03-13 |
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