WO2019096223A1 - Moteur applicable à un outil électrique portatif, et outil électrique portatif - Google Patents

Moteur applicable à un outil électrique portatif, et outil électrique portatif Download PDF

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Publication number
WO2019096223A1
WO2019096223A1 PCT/CN2018/115725 CN2018115725W WO2019096223A1 WO 2019096223 A1 WO2019096223 A1 WO 2019096223A1 CN 2018115725 W CN2018115725 W CN 2018115725W WO 2019096223 A1 WO2019096223 A1 WO 2019096223A1
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WO
WIPO (PCT)
Prior art keywords
stator
motor
outer diameter
hand
power tool
Prior art date
Application number
PCT/CN2018/115725
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English (en)
Chinese (zh)
Inventor
赵晓
周中亚
毋宏兵
吴海全
卞印航
李伟锋
卢惠
李辉
张伟
Original Assignee
苏州宝时得电动工具有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN201721525916.4U external-priority patent/CN207652226U/zh
Application filed by 苏州宝时得电动工具有限公司 filed Critical 苏州宝时得电动工具有限公司
Priority to US16/205,284 priority Critical patent/US11027405B2/en
Publication of WO2019096223A1 publication Critical patent/WO2019096223A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B23/00—Portable grinding machines, e.g. hand-guided; Accessories therefor
    • B24B23/02—Portable grinding machines, e.g. hand-guided; Accessories therefor with rotating grinding tools; Accessories therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/02—Construction of casings, bodies or handles
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K27/00—AC commutator motors or generators having mechanical commutator

Definitions

  • the present invention relates to a motor for use in a hand-held power tool, and a hand-held power tool using the same.
  • the power tool is a working tool that is driven by a motor to move the working head to perform cutting, drilling, grinding, etc. on the workpiece.
  • Hand-held power tools such as angle grinders, swing machines, electric circular saws, etc., require the user to operate with a hand tool.
  • the best working condition of this type of hand-held power tool is that the user can grasp the tool case with one hand, while the other hand can be used to assist the control or the movement direction, force and angle adjustment of the work head.
  • the motor In a hand-held AC power tool such as an angle grinder, an oscillating machine or an electric circular saw, the motor is usually installed in the middle of the casing of the machine, and the user usually grasps the position in the middle of the casing during use, which is beneficial to the operation process.
  • Balance control; the weight and size of the motor will directly affect the volume of the case, affecting the user's grip experience when using the power tool.
  • the motor is not installed in the holding position, which requires re-laying the weight of the tool so that the main weight source of the power tool is placed at the front and rear ends of the holding part during operation. This is beneficial to the balance control of the power tool operation and the labor saving.
  • the size of the large-function motor will increase, and accordingly, the size of the casing portion accommodating the motor is increased accordingly. It will also increase the difficulty for the user to grasp, and it is easy to cause unstable grip and fatigue. If a small power motor is selected, although the size of the motor is reduced, the size of the casing housing the motor can be reduced, but the power of the power tool is also reduced, which cannot meet the user's demand for working conditions. It is necessary to meet the requirements of high-power working conditions and the handling operation. This is a contradiction that has long plagued the skilled person in the field.
  • a split stator motor is also used in the prior art to replace the conventional integral motor.
  • the so-called split type motor is that the stator is divided into multiple pieces before winding, and each individual winding can increase the amount of winding, and then splicing or welding each piece after winding the line.
  • the split stator can coil more coils than the integral stator, thereby increasing the power of the motor.
  • the manufacturing and assembly process of the split stator is more complicated than the one-piece stator, and the manufacturing cost is much higher, which is not suitable for widespread use in power tool products.
  • the wall thickness of the power tool casing and the clearance between the casing and the motor may have some influence on the casing to be held, but usually the material of the casing is ordinary plastic, if the wall thickness is reduced, the machine will be significantly reduced.
  • the strength of the shell makes the stability of the power tool work greatly compromised. If the metal casing is used to make the casing, the weight of the whole machine will be significantly improved, and the user's grip and operability will be lowered. If the gap between the casing and the motor is reduced, the heat dissipation space around the motor will be reduced, which is not conducive to heat dissipation of the motor and the casing.
  • the suitable size of the casing will make the user more comfortable to grip and not fatigue, and the grip is strong, the working head can be easily adjusted, and it is not easy to get rid of the hand.
  • the palms of the East Asian yellow race are smaller than the European and American white races.
  • the length of Chinese male palm is usually between 175mm and 200mm, and the width is between 80mm and 90mm.
  • the length of female palm is usually between 150mm and 180mm, and the width is between 65mm and 80mm.
  • the optimal circumference of the hand-held power tool for the user to grasp is between 150mm and 185mm. Power tool manufacturers have been working on portable, hand-held AC power tools that are suitable for the user's grip.
  • the motor used in the hand-held power tool comprises an integral stator; a rotor arranged in the stator; the armature shaft is fixedly connected with the rotor and connected with a commutator; The commutator is electrically connected; the outer diameter of the stator is not more than 58 mm, the ratio of the outer diameter of the rotor to the outer diameter of the stator is in the range of 0.6 to 0.7, and the ratio of the output power to the volume of the motor is greater than 8.5 W/cm 3 .
  • the outer diameter of the stator is no more than 50 mm, and the ratio of the outer diameter of the rotor to the outer diameter of the stator ranges from 0.6 to 0.65.
  • the yoke of the stator has a width ranging from 3.6 mm to 4.2 mm.
  • the length of the stator along the axial direction of the armature shaft is not less than 40 mm.
  • the diameter of the armature shaft is not less than 7.5 mm.
  • the diameter of the armature shaft ranges from 7.5 mm to 9 mm.
  • the invention increases the ratio of the stator to rotor outer diameter of the motor to 0.6 or more, and increases the ratio of the output power of the motor to the volume of 8.5 W/cm 3 or more, thereby enhancing the output capability of the motor of the same size.
  • the motor is used in a hand-held power tool, the motor comprises: a stator, which is integral; the rotor is coaxially sleeved in the stator; the armature shaft is fixedly connected with the rotor; the commutator is fixedly connected with the armature shaft
  • the brush is electrically connected to the commutator; the outer diameter of the stator is not more than 58 mm, the yoke width of the stator ranges from 3.5 mm to 4.2 mm, and the ratio of the outer diameter of the rotor to the outer diameter of the stator ranges from 0.618 to 0.65.
  • the outer diameter of the stator is no more than 55 mm
  • the yoke width of the stator ranges from 4.1 mm to 4.3 mm
  • the ratio of the outer diameter of the rotor to the outer diameter of the stator ranges from 0.618 to 0.636.
  • the stator has an outer diameter of 55 mm, the stator has a yoke width of 4.2 mm, and the rotor outer diameter to stator outer diameter ratio ranges from 0.636.
  • the outer diameter of the stator is no more than 50 mm
  • the yoke width of the stator ranges from 3.8 mm to 4.2 mm
  • the ratio of the outer diameter of the rotor to the outer diameter of the stator ranges from 0.62 to 0.64.
  • the outer diameter of the stator is 50 mm
  • the yoke width of the stator ranges from 3.8 mm
  • the ratio of the outer diameter of the rotor to the outer diameter of the stator ranges from 0.62.
  • the outer diameter of the stator is no more than 46 mm
  • the yoke width of the stator ranges from 3.5 mm to 3.7 mm
  • the ratio of the outer diameter of the rotor to the outer diameter of the stator ranges from 0.62 to 0.65.
  • the outer diameter of the stator is 46 mm
  • the yoke width of the stator is 3.6 mm
  • the ratio of the outer diameter of the rotor to the outer diameter of the stator is 0.62.
  • the invention provides a hand-held power tool suitable for holding and comfortable operation.
  • the hand-held power tool has the above-mentioned integral motor, and further comprises a casing; the transmission mechanism transmits the torque of the armature shaft to the output shaft; the casing has a grip
  • the inner edge of the grip portion at least axially houses the stator, and the outer periphery of the grip portion is used for gripping, and the peripheral circumference of the grip portion ranges from 150 mm to 185 mm, and the output power of the motor and the periphery of the grip portion are The ratio of circumference is greater than 5.1 W/mm.
  • the peripheral circumference of the grip portion ranges from 165 mm to 182 mm, and the outer diameter of the stator is no more than 50 mm.
  • the ratio of the power of the motor to the peripheral circumference of the grip is greater than 5.2 W/mm.
  • the ratio of the power of the motor to the peripheral circumference of the grip is greater than 5.35 W/mm.
  • the peripheral circumference of the grip portion ranges from 165 mm to 170 mm, the outer diameter of the stator is not more than 46 mm, and the length of the stator along the axial direction of the armature shaft is not less than 50 mm.
  • the ratio of the output power of the motor to the peripheral circumference of the grip is greater than 5.15 W/mm.
  • the diameter of the armature shaft is not less than 7.5 mm.
  • the diameter of the armature shaft ranges from 7.5 mm to 9 mm.
  • the casing includes a fuselage and a head casing
  • the fuselage is fixedly coupled to the head casing
  • the grip portion is on the fuselage
  • the fuselage includes a heat dissipating portion
  • the grip portion is located between the head casing and the heat dissipating portion.
  • the cross-sectional area of the grip portion is smaller than the cross-sectional area of the heat dissipating portion.
  • the material of the fuselage is a plastic that has undergone a granulation process.
  • the heat dissipating portion has an air inlet port on the side surface, and the air inlet port extends from one end of the heat dissipating portion to the other end along the length direction of the heat dissipating portion.
  • the head casing has an air outlet, and the ratio of the area of the air inlet to the area of the air outlet is not less than one.
  • the casing includes a connecting portion, and the holding portion is connected to the heat radiating portion through the connecting portion.
  • the hand-held power tool further includes a component disposed at the rear end of the fuselage, a tail cover sleeved at the rear end of the fuselage, and a guiding member between the fuselage and the tail cover, and the tail cover is provided with
  • the tuyere, the guiding member and the tail cover enclose an air inlet passage, and the air inlet passage communicates with the air inlet and the motor, and the cooling air entering the air inlet port flows along the air inlet passage to the motor, and the component is located outside the air inlet passage.
  • the inlet passage and components are located on different sides of the guide.
  • the guide member is disposed on the body.
  • the guide member is integrally formed with the body, or the guide member is fixedly coupled to the body.
  • the guide member is disposed on the tail cover.
  • the guide member is in the form of a plate.
  • the guide member is parallel to the axial direction of the motor.
  • the guide member extends in the axial direction of the motor, and the guide member has a curved surface in a section perpendicular to the axial direction of the motor.
  • the air inlet passage extends in the axial direction of the motor.
  • the air inlet on the tail cover includes a first air inlet that allows cooling air to enter the air inlet passage in the axial direction of the motor, and a second air inlet that enters the air inlet passage in a direction perpendicular to the axial direction of the motor. Inlet.
  • the invention increases the ratio of the output power of the hand-held power tool to the holding circumference to 5.1 W/mm or more, and the output power can fully satisfy the hand tool under the condition of ensuring the comfort of the grip. Job requirements. This not only facilitates the user to use the hand-held power tool for a long time, is not easy to fatigue, and improves work efficiency.
  • the cooling air entering the air inlet flows along the air inlet passage to the motor, and the components are located outside the air inlet passage, so that the cooling air entering the air inlet does not flow through the components, thereby preventing the cooling air from being
  • the components block and form a vortex, so that the cooling air entering the air inlet flows more toward the motor, which improves the effective cooling air volume and cooling efficiency.
  • a hand-held power tool includes: a housing; an output shaft for mounting the working head, the output shaft is mounted in the housing and extends out of the housing; the transmission mechanism is installed in the housing, and the transmission mechanism is connected to the output shaft
  • the motor is installed in the housing, comprising: a stator, the stator is integral; the rotor is coaxially sleeved in the stator; the armature shaft is fixedly connected with the rotor; the armature shaft is connected with the transmission mechanism, and the transmission mechanism is The rotary motion of the armature shaft is converted into a reciprocating motion of the output shaft around its own axis; wherein the outer diameter of the motor ranges from 40 mm to 50 mm, and the bare metal idle speed of the motor is greater than 20000 rpm, and the motor output power
  • the ratio to volume is greater than 2 W/cm3.
  • the housing is provided with a grip portion having an outer circumference of 150 mm to 200 mm.
  • the ratio of the output power of the motor to the peripheral circumference of the grip is greater than 0.8 W/mm.
  • the ratio of the output power of the motor to the peripheral circumference of the grip is greater than 0.95 W/mm.
  • the bare metal no-load speed of the motor is greater than 30,000 rpm, and the motor output power to volume ratio is greater than 5.5 W/cm3.
  • the housing is provided with a grip portion having an outer circumference of 150 mm to 200 mm, and the ratio of the output power of the motor to the peripheral circumference of the grip portion is greater than 2.0 W/mm.
  • the ratio of the outer diameter of the rotor to the outer diameter of the stator ranges from 0.60 to 0.70, and the width of the stator yoke is from 3.5 to 4.0 mm.
  • the ratio of the outer diameter of the rotor to the outer diameter of the stator ranges from 0.65 to 0.70, and the width of the stator yoke is from 3.5 to 3.8 mm.
  • the stator has an outer diameter of 46 mm, a yoke width of 3.6 mm, and a rotor outer diameter to stator outer diameter ratio of 0.62.
  • the axial length of the motor ranges from 45 mm to 60 mm.
  • Figure 1 is a schematic view of the front view of the angle grinder.
  • Figure 2 is a cross-sectional view showing the internal structure of the angle grinder.
  • Figure 3 is a schematic view of the angular grinding in and out of the wind.
  • Figure 4 is a cross-sectional view taken along line I-I of Figure 2;
  • Figure 5 is a schematic view of a conventional motor.
  • Figure 6 is a cross-sectional view taken along line II-II of Figure 2;
  • Figure 7 is a schematic diagram of a high slot full rate motor in which the armature shaft diameter is increased.
  • Figure 8 is a cross-sectional view taken along line III-III of Figure 1.
  • Figure 9 is a schematic exploded view of the angle grinder.
  • Figure 10 is a perspective view of the swinging machine of the present invention.
  • Figure 11 is a cross-sectional view taken along line IV-IV of Figure 10.
  • Figure 12 is a perspective view of the transmission mechanism of the swinging machine of the present invention.
  • the hand-held power tool is an angle grinder 100.
  • the angle grinder 100 has a hollow casing 1 in which a motor 3 and a transmission mechanism 4 are housed, and an air flow passage for cooling is provided.
  • the casing 1 includes a fuselage 11, a tail cover 150 and a head casing 12.
  • the fuselage 11 and the head casing 12 are fixedly connected by screws, thereby ensuring the stability of the hand-held angle grinder during operation, and the tail cover 150 is set and machined.
  • the motor 3 is disposed in the body 11, and the transmission mechanism 4 is disposed in the head casing 12.
  • the motor 3 is a brushed AC motor. In this embodiment, a single-phase series motor is used.
  • the stator 31 includes a stator core 311 and a field winding 312.
  • the rotor 32 includes a rotor core 321, an armature winding 322, and a commutator. 37 and the armature shaft 33, an insulating wrap shaft or the like is usually disposed between the rotor core and the armature shaft.
  • the field winding 312 and the armature winding 322 are connected in series by a brush 34 and a commutator 37.
  • the cooling fan 35, the motor 3, the brush 34, the circuit board (not shown), and the switch 36 are sequentially housed in the body 11 along the axial direction of the armature shaft 33, and the trigger button 36a of the switch 36 is extended to the body 11. External for easy operation.
  • the cooling fan 35 is adjacent to the body 11 of the head casing 12, and the brush 34 is disposed on the brush holder connected to the body 11, and is electrically connected to the commutator 37 of the motor 3.
  • the stator 31 of the present embodiment is an integral stator. Different from the split stator in the prior art, each laminated piece of the stator in the axial direction is hollow and integral, and a plurality of laminated pieces are pressed and welded together to form Hollow monolithic stator.
  • the stator 31 is fixed in the body 11, and the rotor 32 and the armature shaft 33 driven by the rotor 32 are located inside the stator 31, and the armature shaft 33 extends from the end of the cooling fan 35 outside the body 11 to enter the head shell.
  • the body 11 has an approximately cylindrical shape extending along the axial direction of the armature shaft 33, and the extending axis of the body 11 is coaxial with the axis of the armature shaft 33.
  • the body 11 includes a first cylindrical portion 110 for housing the cooling fan 35 and connected to the head case 12, a second cylindrical portion 112 connected to the first cylindrical portion 110, and a commutator 37, a circuit board, and a switch.
  • the diameter of the second tubular portion 112 is smaller than the first one.
  • the diameters of the tubular portion 110 and the third tubular portion 130 are designed such that the grip portion gripped by the user during operation is the thinnest portion of the body 11, and the brush 34 and the cooling fan 35 are respectively located on both sides of the grip portion.
  • the cooling fan 35 is fixedly connected to one end of the armature shaft 33 near the head casing 12, and generates a negative pressure when rotating, and the cooling air outside the casing 1 is sucked through the air inlet 1151 of the tail cover 150, and flows through the switch 36, the circuit board, and the motor. 3.
  • the cooling fan 35 is discharged from the air outlet 121 of the head casing 12.
  • the diameter of the first cylindrical portion 110 is larger than the diameter of the second cylindrical portion 112 as the grip portion, the diameter of the cooling fan 35 disposed in the first cylindrical portion 110 may also be set larger than the diameter of the stator 31, and cooled.
  • the air intake is large and the cooling effect is good.
  • the first tubular portion 110 includes an enlarged portion 117 and a transition portion 118 that is connected to the second tubular portion 112 and has a curved surface.
  • the angle ⁇ between the transition portion 118 and the grip portion is close to 120°.
  • the setting of the angle ⁇ allows the palm of the hand to be engaged with the transition portion 118 when the user holds the operation, so that the transition portion 118 provides stable support for the gripping operation, thereby making the operation more comfortable.
  • the enlarged portion 117 is used for a connection that matches the shape of the head shell 12.
  • the diameter of the cooling fan 35 is set to be equal to the diameter of the stator 31, and the diameter of the first cylindrical portion 110 may also be set to be substantially equal to the diameter of the grip portion 112.
  • the third tubular portion 130 includes a connecting portion 116 connected to the grip portion, and a heat dissipating portion 115 connected to the connecting portion, and the heat dissipating portion 115 provides a passage for the cooling air to enter the air body.
  • the low temperature air outside the casing can enter the casing.
  • the brush 34 is disposed in the connecting portion 116, and may be partially disposed in the connecting portion 116, partially disposed in the heat radiating portion 115, or may be disposed in the heat radiating portion 115.
  • the heat radiating portion 115 is disposed on the body 11 and communicates with the airflow inside the grip portion.
  • the airflow in the heat radiating portion 115 can flow into the grip portion to take away the heat generated by the motor 3.
  • the thickness of the housing of the grip portion and the heat dissipating portion 115 is approximately the same, and the cross-sectional area of the inner edge of the grip portion may be smaller than the cross-sectional area of the inner edge of the heat dissipating portion 115.
  • the cooling air enters from the air inlet 1151 of the heat radiating portion 115, flows through the gap between the grip portion and the motor 3, takes away heat of the motor 3 and the grip portion, and finally flows out from the air outlet 121 of the head casing 12.
  • the cooling air mainly dissipates heat from the motor 3 and the grip portion, reduces the temperature of the motor 3 and the grip portion, and prevents the internal temperature of the hand-held angle grinder from being too high, thereby affecting the working and service life of the components therein.
  • the head casing 12 and the transmission mechanism 4 are also dissipated as they flow through the head casing 12. When the tail cover 150 is sleeved on the body 11, the heat dissipating portion partially overlaps with the tail cover.
  • the air inlet 1151 and the tail cover 150 are respectively provided with air inlets 1151.
  • the air inlets 1151 include a plurality of slots (not labeled) extending along the axial direction of the heat dissipation portion 115 and spaced apart from each other in the radial direction. As a cooling passage, it enters the inside of the casing with low temperature air. In the present embodiment, the air inlet 1151 extends from one end of the heat radiating portion 115 to the other end.
  • On the inner side of the casing of the tail cover 150 there are respectively inserted and inserted dustproof sheets 22, and the dustproof sheets 22 are provided with a fine grid for external airflow, but can prevent dust having a certain granularity from entering.
  • the inside of the casing; the dustproof piece 22 is arranged to facilitate cleaning and installation, and can effectively prevent dust from entering the air inlet 1151.
  • the motor 3 is disposed in the body 11, wherein the stator 31 is interference-fitted with the fixing member 113 in the body 11, ensuring that there is no relative movement between the stator 31 and the body 11, wherein the fixing member 113 and the holding portion are The edges are integrally formed.
  • the rotor 32 is disposed in the stator 31, and both ends of the armature shaft 33 are respectively installed in the first bearing 331 and the second bearing 332, wherein the first bearing 331 is disposed in the first bearing chamber 111 in the body 11, and the second The bearing 332 is disposed in the second bearing chamber 122 of the head case 12.
  • a first mounting portion having approximately the same contour is extended from the first tubular portion 110, and the head casing 12 has a second mounting portion having approximately the same contour, and the first mounting portion is identical to the second mounting portion when assembled
  • the shafts are connected together, and then the body 11 and the head case 12 are fixedly connected by screws.
  • the first mounting portion is coaxial with the first bearing chamber 111, and the second mounting portion is also coaxial with the second bearing chamber 122, thereby securing the first bearing chamber 111 and the second bearing chamber 122 remains coaxial.
  • the material of the fuselage 111 is subjected to a granulation process.
  • Plastics by increasing the glass fiber content, the tensile strength is greater than 200Mpa, the bending strength is greater than 250Mpa, the moisture absorption rate is less than 2%, and the strength stability is high.
  • the dimensional stability of the plastics that meet the above parameters can prevent large deformation of the fuselage and affect the coaxiality of the stator and the rotor.
  • the transmission mechanism 4 located in the head casing 12 includes an angled bevel gear set including a tapered pinion 41 coupled to the armature shaft 33, a conical bull gear 42 coupled to the output shaft 2, an output shaft 2 and an armature
  • the shaft 33 is disposed substantially vertically.
  • the diameter of the second tubular portion 112 determines the circumference of the grip portion, and the circumference of the grip portion directly affects the grip feeling of the user. If the circumference of the grip portion is too long, the grip of the user is unstable, and the operation is easy. fatigue. According to the test, the length of the Chinese male palm is usually between 175mm and 200mm, and the width is between 80mm and 90mm. The length of the Chinese female palm is usually between 160mm and 180mm, and the width is between 65mm and 80mm. When grasping the hand-held angle grinder, the length of the palm surrounds the grip portion. Generally, the circumference of the grip portion should be slightly larger or slightly smaller than the length of the palm.
  • the second tube portion also houses the motor. Considering the support structure of the motor, the air passage, and the like, the diameter of the motor should be no more than 58 mm.
  • the axial length L of the motor 3 is defined by the length of the stator core 311 or the length of the rotor core 321 , and generally the axial length L of the stator core 311 and the rotor core 321 are the same.
  • the rotation speed of the motor 100 of the angle grinder 100 is required to reach about 38000 rpm.
  • the power input from the grid to the angle grinder 100 during operation is defined as the input power P1;
  • the output power P2 of the motor 3 is proportional to the diameter D of the motor 3, the axial length L of the motor 3, the rotational speed of the motor, and the slot full rate of the motor.
  • the speed of the motor is basically not affected by the safety regulations and the life of the motor. If it is considered to increase the diameter D of the motor 3 in order to increase the output power P2 of the motor, it is necessary to increase the diameter of the grip portion correspondingly, which makes it difficult for the user to grasp.
  • the rotor core 321 and the stator core 311 are usually laminated stacks which are stacked and welded in the axial direction with an appropriate number of metal laminations, and the main component is iron, so it may also be referred to as an iron core.
  • each laminated piece of the monolithic stator in the axial direction is hollow and integral, rather than being spliced by a plurality of small laminations.
  • the thickness of the metal lamination is 0.5 mm
  • the axial length of the stator core 311 and the rotor core 321 is the total thickness of the appropriate number of lamination stacks.
  • the outer profile of the unitary stator may be arranged in a circular, elliptical, rectangular or other shape suitable for accommodation in the casing.
  • Each metal lamination of the stator core 311 is provided with a notch 313, and each metal lamination of the rotor core 321 is provided with a notch 323; thus, a lamination stack formed by a metal lamination of the stator core 311, respectively
  • the lamination stack formed by the metal laminations of the rotor core 321 is respectively formed with slots, and coils are respectively wound in the stator core slots and the rotor core slots.
  • FIG. 5 there is a cross section of a conventional motor in which the coils wound in the stator and rotor slots are substantially sparse, and usually a screw hole 315 for fixing the stator to the casing is provided, and the screw holes are provided.
  • the presence of 315 reduces the stator yoke width 311a, which in turn affects the stator core slot size and the coils therein.
  • the stator 31 and the body 11 of the embodiment of the present invention adopt different fixing methods, the screw holes are eliminated, the size of the stator core slot is not affected, and the number of turns of the coil is large and the winding is tight. .
  • the result is that the more the coil area is wound in the unit slot area, the higher the tank full rate, and the greater the magnetic field strength of the motor, the larger the output power P2 of the motor.
  • the overall weight of the motor 3 is increased, and in particular, the weight of the rotor 32 is increased, which increases the load on the armature shaft 33 of the rotor 32.
  • the rotor 32 of the motor is disposed in a space surrounded by the stator 31, and has a radial gap of substantially 0.5 mm or less with the stator 31. Therefore, the coaxiality between the rotor and the stator is very high, and slight deviation causes the rotor to rotate. Rubbing against the stator, or called a broom. Brooms generate a lot of heat and can burn out the motor or cause more serious accidents.
  • the armature shaft 33 of the rotor 32 When the armature shaft 33 of the rotor 32 encounters a load, the armature shaft 33 generates a certain bending deformation, and if the load is increased, the amount of deformation increases. In order to prevent the armature shaft 33 from causing a large deformation to cause the broom, it is necessary to reduce the amount of deformation of the armature shaft 33 when subjected to the load, that is, to reduce the deflection of the armature shaft 33. The diameter of the armature shaft 33 needs to be increased without changing the material of the armature shaft 33.
  • the diameter of the armature shaft 33a is increased to reduce the size of the rotor yoke width 322a, thereby reducing the magnetic flux of the rotor, thereby Reduce the output power of the motor; the diameter of the armature shaft increases, and the magnetic flux of the rotor decreases, which is a contradiction between the two.
  • the invention proposes that while improving the winding process of the motor, the carrying capacity of the armature shaft 33 and the output power of the motor should be ensured at the same time.
  • Table 1 shows the comparison of the data for the impact of the armature shaft diameter on the motor power performance when the speed of the motor meets the requirements of the hand angle grinder at 38000 rpm. Since the test machine is difficult to stabilize the speed at 38,000 rpm, the actual test speed will be slightly greater than 38000 rpm, so that the measured result is within an acceptable range. In addition, since the test motor requires a carrier to fix the motor and apply a load to the motor, the motor is tested in a hand-held power tool, such as in an angle grinder.
  • the reference sample has an armature shaft diameter of 7.5 mm and a power of 975 W.
  • the four measurement samples are compared to the reference sample, wherein the diameter of the armature shaft increases equally.
  • the diameter of the reference armature shaft is increased by 7.5 mm and the diameter of the motor is increased by 1%.
  • the loss rate of the motor power is below 3%. Compared with the working requirements of the hand-held angle grinder, the loss rate is within the acceptable range.
  • the diameter of the armature shaft exceeds 9.5 mm, the loss of motor power will increase, and the motor power is only 85% of the reference sample.
  • the diameter of the armature shaft is not less than 7.5 mm, in order to ensure the motor power and the bearing capacity of the armature shaft; in one embodiment, the diameter of the armature shaft 33 ranges from 7.5 mm to 9 mm, so that the motor can be ensured. The power meets the demand and ensures that the motor works properly.
  • stator yoke width 311a the area between the stator slot and the outer diameter of the stator is defined as the stator yoke width 311a.
  • the stator yoke width 311a affects the magnetic flux of the stator. The larger the stator yoke width 311a is, the larger the magnetic flux is, and the larger the output power P2 of the motor is. .
  • a slot for winding the coil and an inner diameter hole embedded in the rotor are required on the stator lamination; referring to Fig. 5, the stator lamination usually also leaves a screw hole 315 for fixing the stator to the casing.
  • the present embodiment changes the cooperation between the stator 31 and the body 11 into an interference fit, cancels the screw hole, and increases the width of the stator yoke width 311 to 3.6 mm or more.
  • the range of stator yoke widths is set between 3.6 mm and 4.2 mm to further increase the slot size for winding more coils to increase magnetic flux.
  • the inner diameter hole of the stator 31 is used to embed the rotor 32, and a gap is maintained between the stator 31 and the rotor 32 to ensure that the rotor does not rub against the stator when the rotor rotates at a high speed, the inner diameter hole of the stator 31 increases, and the diameter of the rotor 32 can be correspondingly increased. Can increase the magnetic flux of the rotor. However, an increase in the inner diameter of the stator 31 also reduces the size of the stator yoke width 311a, which in turn reduces the magnetic flux of the stator 31. The inner diameter of the stator increases, and the magnetic flux of the stator decreases, which in turn is a contradiction between objective and objective.
  • the present invention studies the influence of the stator and rotor outer diameter ratios on the output power of the motor, and solves the relationship between the power and the outer diameter of the stator and the rotor.
  • Table 2 shows the variation of the motor power to volume ratio under the condition that the stator diameter is 50 mm and the axial length of the motor is 50 mm, the stator yoke width is different, and the stator and rotor outer diameter ratios are changed.
  • the values in Table 2 show the same motor volume, the stator yoke width increases or the stator and rotor outer diameter ratios increase, and the power of the motor exhibits an undulating change.
  • the ratio of the outer diameter of the stator to the rotor is 0.62
  • the ratio of power to volume reaches a maximum value of 10.05 when the stator yoke width is 3.8 mm.
  • the ratio of power to volume is 0.62 in the stator to rotor outer diameter ratio.
  • the maximum value of 10 was reached.
  • the yoke width of the stator ranges from 3.8 mm to 4.2 mm, and the ratio of the outer diameter of the rotor to the outer diameter of the stator ranges from 0.62 to 0.64, and the power-to-volume ratio of the motor is relatively large, especially the yoke width of the stator.
  • the range is 3.8mm, and the motor's power-to-volume ratio is the largest when the ratio of rotor outer diameter to stator outer diameter is 0.62.
  • the ratio of the power to the volume of the motor is a value that reflects the power output efficiency of the motor. Under the same volume, the larger the ratio, the greater the motor power.
  • the power of the motor in Table 2 refers to the power value when the motor speed reaches 38000 rpm.
  • the ratio of the stator to the outer diameter of the rotor and the width of the stator yoke all affect the ratio of motor power to volume. The larger the stator and rotor outer diameter ratio is, the larger the rotor size is, and the stator yoke width 311 is correspondingly reduced; vice versa. The larger the stator yoke width, the smaller the stator slot and rotor size, and vice versa.
  • Reasonable design, rotor outer diameter ratio and yoke width can make the motor power reach a larger value.
  • the ratio of motor power to volume is selected to be greater than 8.5, so that the grip angle of the hand-held angle grinder is comfortable and more powerful under the same motor volume, especially the same stator diameter.
  • the stator yoke width increases or the stator and rotor outer diameter ratios increase, and the power of the motor exhibits an undulating change.
  • the stator to rotor outer diameter ratio ranges from 0.6 to 0.7 and the outer diameter of the stator is no greater than 58 mm.
  • the outer diameter of the stator is no more than 50 mm.
  • the stator to rotor outer diameter ratio ranges from 0.6 to 0.65 and the yoke width ranges from 3.6 mm to 4.2 mm. The yoke width is excessively reduced to reduce the area of the slot, resulting in a reduction in the amount of stator winding.
  • the power of the motor fluctuates within a range close to the maximum.
  • the axial length of the motor that is, the length of the stator along the axial direction of the armature shaft is set to be not less than 40 mm, and the setting range is 45 mm to 60 mm, preferably 55 mm.
  • the ratio of the output power P2 of the motor 3 to the peripheral circumference of the angle grinder grip is greater than 5.1 W/mm, where the output power P2 is the maximum output power of the angle grind input to the work object.
  • the grip of the hand-held angle grinder 1 has a peripheral circumference of 150 mm to 185 mm. In order to allow sufficient space inside the grip to accommodate the motor 3, the outer diameter of the stator 31 is no more than 58 mm.
  • the peripheral circumference of the grip portion of the hand-held angle grinder 100 is set to 165 mm to 182 mm, and the outer diameter of the stator 31 is not more than 50 mm.
  • the axial length L of the motor is not less than 40 mm, and the ratio of the output power P2 of the motor 3 to the peripheral circumference of the angle grinder grip portion is larger than 5.2 W/mm.
  • the ratio of the output power P2 of the motor 3 to the peripheral circumference of the angle grinder grip is greater than 5.35 W/mm.
  • the material of the head shell 12 of the hand-held angle grinder 100 is usually made of metal, mainly aluminum, and has high strength.
  • the second bearing chamber 122 does not undergo large deformation, affecting the rotor 32 and the stator.
  • the body 11 is made of plastic, and the first bearing chamber 111 is integrally formed on the body 11. In order to ensure sufficient strength of the body 11, the first bearing chamber 111 and the fixing member 113 are prevented from being deformed greatly, and the stator is affected. Concentricity with the rotor.
  • the material of the fuselage 11 is a granulated plastic.
  • the tensile strength is greater than 200 MPa
  • the bending strength is greater than 250 MPa
  • the moisture absorption rate is less than 2%
  • the strength is stable. High sex.
  • the dimensional stability of the plastics that meet the above parameters can prevent large deformation of the fuselage and affect the coaxiality of the stator and the rotor.
  • Both the grip portion and the heat radiating portion 115 have a substantially cylindrical shape, and extend in the axial direction of the armature shaft 33, and the longitudinal direction of the grip portion and the heat radiating portion 115 is the same as the axial direction of the armature shaft 33.
  • the designer needs to consider the area relationship between the two, usually the air inlet area is larger than the air outlet.
  • the larger the air inlet the larger the ideal air intake, but if it is too large, the cooling air will lose its guidance, forming a flow around the air inlet, entering from the air inlet and then flowing out from the air inlet, or the cooling air cannot be smooth.
  • the ground discharge causes the cooling efficiency to decrease.
  • the ratio of the area of the air inlet to the area of the air outlet is greater than 1, and the preferred range is 1.2 to 1.4.
  • the peripheral portion of the grip of the hand-held angle grinder 100 has a circumference of 165 mm to 170 mm, the length of the stack of laminations is not less than 50 mm, and the outer diameter of the stator is no more than 46 mm.
  • the ratio of the output power P2 of the motor 3 to the peripheral circumference of the angle grinder grip is greater than 5.15 W/mm.
  • the diameter of the armature shaft is set to be not less than 7.5 mm.
  • Table 3 shows the variation of the motor power to volume ratio under different conditions of stator and rotor outer diameter when the stator diameter is 46 mm. Similar to the test results of Table 2, the values in Table 3 show the same motor volume, the stator yoke width increases or the stator and rotor outer diameter ratios increase, and the power of the motor exhibits an undulating change.
  • the ratio of the outer diameter of the stator to the rotor is 0.62
  • the ratio of power to volume reaches a maximum value of 10.2 when the stator yoke width is 3.6 mm; when the stator yoke width is 4 mm, the ratio of power to volume is 0.62 in the stator to rotor outer diameter ratio. The maximum value of 8.6 was reached.
  • the yoke width of the stator ranges from 3.5 mm to 3.7 mm, and the ratio of the outer diameter of the rotor to the outer diameter of the stator ranges from 0.62 to 0.65, and the power-to-volume ratio of the motor is relatively large, especially the yoke width of the stator.
  • the range is 3.6mm, and the ratio of the outer diameter of the rotor to the outer diameter of the stator is 0.62.
  • the ratio of power to volume of the motor is the largest.
  • the diameter of the armature shaft is set between 7.5 mm and 9 mm, preferably 8 mm.
  • the stator diameter of the motor is 55 mm
  • the peripheral circumference of the grip portion of the angle grinder for housing the motor is larger
  • the power of the motor is also increased.
  • Table 4 shows different stators when the stator diameter is 55 mm.
  • the yoke width is the change of the motor power to volume ratio under the condition that the stator and rotor outer diameter ratios are changed. With the same motor volume, the stator yoke width increases or the stator and rotor outer diameter ratios increase, and the power of the motor exhibits an undulating change.
  • the yoke width of the stator ranges from 4.1 mm to 4.3 mm, and the ratio of the outer diameter of the rotor to the outer diameter of the stator ranges from 0.618 to 0.636, and the power-to-volume ratio of the motor is relatively large, especially the yoke width of the stator.
  • the range is 4.2mm, and the ratio of the outer diameter of the rotor to the outer diameter of the stator is 0.636.
  • the ratio of power to volume of the motor is the largest.
  • the increase of the power of the motor will cause more heat during the operation of the motor.
  • the reduction of the diameter of the grip will reduce the area of the heat dissipating air passage.
  • the length of the lamination stack will lengthen the heat dissipating air passage. The above factors will cause the motor.
  • the hand-held power tool 100 includes a tail cover 150 that is sleeved at the rear end of the body 11 and a guide 170 that is located between the body 11 and the tail cover 150. Wherein, the guiding member 170 and the tail cover 150 form an air inlet passage 190.
  • the rear end of the casing 110 is provided with a plurality of components 5, and the plurality of components 5 are specifically capacitors, switches and the like.
  • the tail cover 150 is provided with an air inlet 1151.
  • the cooling air enters the heat radiating portion 115 from the air inlet port and flows through the motor 3, thereby reducing the heat of the motor 3, thereby achieving the purpose of heat dissipation.
  • the air inlet 1151 on the tail cover 150 includes a first air inlet 151 for allowing cooling air to enter the air inlet passage along the axial direction of the motor 3, and the cooling air enters the air inlet passage in a direction perpendicular to the axial direction of the motor 3.
  • the second air inlet 153 it is also possible to provide the first air inlet 151 or the second air inlet 153 only on the tail cover 150.
  • the guide member 170 and the tail cover 150 enclose an air inlet passage 190.
  • the air inlet passage 190 extends axially along the motor 3 or at an angle to the axial direction of the motor 3.
  • the air inlet passage 190 is in communication with the air inlet, and the air inlet passage 190 is in communication with the interior of the motor.
  • the cooling air entering the air inlet flows along the air inlet passage 190 to the motor 3.
  • the direction indicated by the arrow in FIG. 8 is the flow direction of the cooling air.
  • the component 5 is located outside the air inlet passage 190.
  • the inlet passage 190 and the component 5 are located on different sides of the guide member 170. That is, the guiding member 170 separates the air inlet passage 190 and the component 5 on both sides of the guiding member 170, so that the cooling air entering the air inlet port no longer flows through the component 5, thereby preventing the cooling air from being blocked by the component 5,
  • the eddy current is formed such that the cooling air entering the air inlet flows more toward the motor 130, improving the effective cooling air volume and cooling efficiency.
  • the heat dissipation effect of the electric tool 100 is enhanced, so that the motor and the casing avoid the phenomenon that the temperature rises due to poor heat dissipation effect, and the comfort of the holding portion of the casing is increased, which is convenient for the operator to operate.
  • the guiding member 170 is disposed on the casing 110.
  • the guiding member 170 may be integrally formed with the body 11 or may be fixedly connected to the body 11, such as welding, screwing, snapping, and the like. If the guide member 170 is integrally formed with the body 11, the side wall of the body 11 can be used as a guide member, as long as the side wall of the housing can be enclosed with the tail cover 150 as the air inlet passage 190.
  • the guide member 170 can also be disposed on the tail cover 150.
  • the guide member 170 can also be integrally formed with the tail cover 150 or fixedly coupled to the tail cover 150, such as welding, screwing, snapping, and the like.
  • the guiding member 170 is of a unitary structure.
  • the guiding member 170 can also be formed by splicing a plurality of sub-guide members.
  • the guide 170 can be in a regular or irregular shape.
  • the guide member 170 is plate-shaped, which facilitates processing and allows the cooling air to circulate smoothly.
  • the guide member 170 is parallel to the axial direction of the motor 3 to make the cooling air flow more smoothly.
  • the guide member 170 extends in the axial direction of the motor 3, and the guide member 170 has a curved surface in a section perpendicular to the axial direction of the motor 3.
  • the guide member 170 is fan-shaped in a section perpendicular to the axial direction of the motor 3.
  • the guiding member 170 is not limited to the above shape, and may have other regular or irregular shapes, as long as the air inlet passage 190 and the component 5 can be separated, so that the cooling air entering the air inlet directly flows to the motor 3 . Instead of flowing through the component 5.
  • the guide member 170 is made of the same material as the body 11.
  • the guide member 170 can also be made of materials of other materials.
  • the guide member 170 is made of a waterproof material to prevent the component 5 from degrading due to moisture.
  • the power tool 100 is an angle grinder.
  • the power tool 100 is not limited to the angle grinder, but may be other types of electric tools that have a motor and dissipate heat by cooling air.
  • the cooling air entering from the air inlet flows to the motor along the air inlet passage, and the component is located outside the air inlet passage, so that the cooling air entering the air inlet does not flow through the component, thereby avoiding The cooling air is blocked by the components to form a vortex, so that the cooling air entering the air inlet flows more toward the motor, which improves the effective cooling air volume and cooling efficiency.
  • a hand-held power tool is an oscillating machine
  • the oscillating machine 600 includes a housing 610 , and a motor 3 received in the housing 610 .
  • the structure of the motor 3 is the same as that of the motor 3 in the angle grinder 100 in the previous embodiment of the present invention. The specific structure is not described here. The difference lies only in the outer diameter of the motor 3 and the bare-metal idle speed (when not installed to the tool). The difference in the no-load speed) is described further in the following description.
  • the housing 610 has a bottom portion opposite to the top portion and two side portions connecting the top portion and the bottom portion.
  • the housing 610 is disposed at one end of the output shaft 30 at two ends.
  • Two sets of air outlets 611 are disposed symmetrically disposed on the housing 610. Left and right sides.
  • the air intake opening 612 of the housing 610 is two sets, and the number of the air inlets 612 of the housing 610 is two sets symmetrically disposed on the left and right ends of the extended end of the housing 610. side.
  • the oscillating machine 600 includes a fan 650 housed in the housing 610.
  • the fan 650 is disposed at a position near the air outlet 611 in a region between the motor 3 and the output shaft 620.
  • the fan 650 is mounted on the armature shaft 33 by electricity.
  • the pivot 33 is driven.
  • the motor 3 drives the armature shaft 33 to rotate, the fan 650 rotates at a high speed under the driving of the armature shaft 33, sucking external cold air from the air inlet 612 at the end of the housing 610, passing through the circuit board 670 and then passing through the entire board.
  • the motor 3 then discharges the air carrying the heat through the air outlet 611 of the housing 610 through the fan 650.
  • the specific fan 650 can select a centrifugal fan, and is arranged to provide better discharge of hot air from the air outlet 611.
  • a transmission mechanism is disposed between the armature shaft 33 and the output shaft 620.
  • the transmission mechanism is an eccentric transmission mechanism 640
  • the eccentric transmission mechanism 640 is disposed in the housing 613, including the shift fork 641 and
  • An eccentric component 642 is attached to the armature shaft 33.
  • the eccentric assembly 642 includes an eccentric shaft 643 coupled to the armature shaft 33 and a drive wheel 644 mounted on the eccentric shaft 643.
  • One end of the shift fork 641 is coupled to the top of the output shaft 620 and the other end is coupled to the drive wheel 644 of the eccentric assembly 642.
  • the shift fork 641 includes a sleeve 645 that is sleeved on the output shaft 620 and a fork 646 that extends horizontally from the top end of the sleeve 645 toward the armature shaft 33.
  • the drive wheel 644 is a ball bearing having a spherical outer surface that mates with the fork portion 646 of the shift fork 641.
  • the eccentric shaft 643 is eccentrically coupled to the armature shaft 33, that is, the axis X3 of the eccentric shaft 643 does not coincide with the axis X2 of the armature shaft 33, and is radially offset by a certain pitch.
  • the forks 646 of the fork 641 are wrapped around the sides of the drive wheel 644 and are in sliding contact with the outer surface of the drive wheel 644.
  • the eccentric shaft 643 is eccentrically rotated relative to the axis X2 of the armature shaft 33 by the armature shaft 33, thereby driving the driving wheel 644 to rotate eccentrically with respect to the axis X2 of the armature shaft 33.
  • the shift fork 641 is swung relative to the axis Y of the output shaft 620 to further oscillate the output shaft 620 about its own axis Y.
  • the output shaft 620 swings to drive the working head mounted thereon to swing the workpiece.
  • the swing angle of the output shaft 620 is 5°.
  • the swing frequency of the output shaft 620 is 18000-20000 rpm.
  • the swing angle of the output shaft 620 is not limited to 5°, and it may be set to a value greater than or less than 5° as needed.
  • the swing frequency of the output shaft 620 is also not limited to 18000-20000 rpm, preferably greater than 10000 rpm.
  • the output shaft 620 is used to mount the working head.
  • the output shaft 620 is mounted on the housing 610 and extends out of the housing 610, which facilitates mounting of the working head (not shown) on the output shaft 620.
  • the motor 3 supplies power to the swinging machine 600, and the power of the motor 3 is transmitted to the output shaft 620 through the transmission mechanism 640, and the swinging machine 600 realizes the swinging operation.
  • Work heads include straight saw blades, circular saw blades, triangular sanding discs and spade scrapers.
  • the housing 610 extends along the axis of the motor 3 and can be divided into a first region 614 that is remote from the output shaft 620 and a second region 615 that is adjacent to the output shaft 620.
  • the first area 614 accommodates the motor 3 and includes a grip portion 630 formed on the outside of the motor 3 for the user to hold, and the power control switch 660 is disposed adjacent to the grip portion 630 or directly disposed on the grip portion 630;
  • the second region 615 then houses the transmission mechanism 140.
  • the oscillating machine 600 of the present invention uses the motor 3 having an outer diameter of between 40 mm and 50 mm to power the oscillating machine 600, and the size of the housing 610 for the grip portion is reduced due to the reduction in the outer diameter of the motor 3.
  • the reduction makes the overall size of the oscillating machine 600 of the present invention small, which is convenient for the operator to hold.
  • the oscillating machine 600 generates vibration during operation, but because of the small size of the whole machine, the grip is comfortable, even if there is vibration. Long-term grip will not make the operator uncomfortable.
  • the circumference of the grip portion of the housing 610 is in the range of 150 mm to 200 mm, so that the operator can hold the swinging machine 600, thereby facilitating the swinging machine. 600 operation to ensure processing efficiency.
  • Table 5 shows that the diameter of the stator is 46 mm, the axial length of the motor is 50 mm, and the bare metal idle speed of the motor 3 is 30,000 rpm (the idle speed when the motor is not mounted on the tool), at different stator yoke widths 331a (Refer to Fig. 4 for the specific structure), the change of motor power to volume ratio under the condition that the stator and rotor outer diameter ratios are changed.
  • the values in Table 5 show that the stator yoke width 331a increases or the stator and rotor outer diameter ratios increase with the same motor volume and no-load speed, and the power of the motor exhibits an undulating change.
  • the ratio of power to volume reaches a maximum value of 5.54 when the stator yoke width 331a is 3.6 mm; when the stator yoke width 331a is 3.7 mm, the ratio of power to volume is in the stator When the outer diameter ratio is 0.62, the maximum value of 5.51 is reached.
  • Table 5 is the experimental data when the stator diameter is 46mm. When the motor is larger and the other parameters are the same, the power-to-volume ratio of the motor will be larger.
  • the ratio of the power to the volume of the motor is a value that reflects the power output efficiency of the motor. Under the same volume, the larger the ratio, the greater the motor power.
  • the motor power in Table 5 is the power value of the motor with a bare metal no-load speed of 30,000 rpm.
  • the ratio of the stator and rotor outer diameters and the stator yoke width 331a all affect the ratio of motor power to volume. The larger the stator and rotor outer diameter ratio is, the larger the rotor size is, and the stator yoke width 331a is correspondingly reduced; vice versa. The larger the stator yoke width 331a, the smaller the stator slot and the rotor size, and vice versa. Reasonable design, rotor outer diameter ratio and yoke width can make the motor power reach a larger value.
  • the ratio of motor power to volume is selected to be greater than 5 W/cm 3 , so that the hand-held swing machine 600 has a comfortable grip and more power under the same motor volume, especially the same stator diameter. Big.
  • the stator yoke width 331a increases or the stator and rotor outer diameter ratios increase, and the power of the motor 3 exhibits an undulating change.
  • the stator to rotor outer diameter ratio ranges from 0.6 to 0.7 and the outer diameter of the stator is no greater than 50 mm.
  • the outer diameter of the stator is 40-50 mm.
  • the stator and rotor outer diameter ratios range from 0.6 to 0.65 and the yoke width ranges from 3.6 mm to 3.8 mm. The yoke width is excessively reduced to reduce the area of the slots, resulting in a reduction in stator winding.
  • the power of the motor 3 fluctuates within a range close to the maximum value.
  • the optimum motor has an outer diameter of 46 mm, a yoke width of 3.6 mm, and a ratio of stator to rotor inner and outer diameter of 0.62.
  • Table 6 shows that the stator has a diameter of 46 mm, the outer circumference of the grip is 198 mm, the axial length of the motor is 50 mm, and the bare motor idle speed is 30,000 rpm (the idle speed when the motor is not mounted on the tool)
  • the values in Table 6 show the same motor volume, no-load speed and the outer circumference of the grip.
  • the stator yoke width 331a increases or the stator and rotor outer diameter ratios increase, and the power of the motor exhibits an undulating change.
  • the ratio of power to outer circumference reaches a maximum value of 2.32 when the stator yoke width 331a is 3.6 mm; when the stator yoke width 331a is 3.7 mm, the ratio of power to volume is determined.
  • the maximum value of 2.16 is reached.
  • the ratio of the power of the motor to the outer circumference of the grip is a value reflecting the power output efficiency of the motor. Under the same outer circumference, the larger the ratio, the larger the output power of the motor.
  • the ratio of the output power of the motor 3 to the peripheral circumference of the grip portion of the oscillating machine 600 is greater than 2.0 W/mm, where the output power refers to the maximum output power of the oscillating machine 600 input to the work object.
  • the outer circumference of the grip portion of the oscillating machine 6001 is 150 mm to 200 mm. In order to have sufficient space inside the grip to accommodate the motor 3, the outer diameter of the stator is 40-50 mm.
  • the peripheral circumference of the grip portion of the oscillating machine 600 is set to 165 mm to 200 mm, and the outer diameter of the stator is 46-48 mm.
  • the ratio of the output power of the motor 3 to the peripheral circumference of the grip portion of the oscillating machine 600 is greater than 2.1 W/mm.
  • the peripheral circumference of the grip portion of the oscillating machine 600 is set to 180 mm and the outer diameter of the stator is 46 mm.
  • the ratio of the output power of the motor 3 to the peripheral circumference of the grip portion of the oscillating machine 600 is greater than 2.3 W/mm.
  • the motor 3 cannot be directly applied to the oscillating machine 600.
  • the motor can be mounted on the oscillating machine by adding a speed stabilizer, and the idle speed of the whole machine is controlled at 20000 rpm, so that the corresponding output shaft 620 rotates at about 20,000 rpm.
  • the specific how to use the speed stabilizer to control the rotational speed of the motor is a conventional means in the art, and will not be described here.
  • Table 7 shows that when the stator diameter is 46 mm and the axial length of the motor is 50 mm, the bare motor idle speed is 20000 rpm (the idle speed when the motor is not mounted on the tool), at different stator yoke widths 331a, The change of the motor power to volume ratio under the condition that the rotor and outer diameter ratios are changed.
  • the values in Table 6 show the same motor volume, the stator yoke width 331a increases or the stator and rotor outer diameter ratios increase, and the power of the motor exhibits an undulating change.
  • the ratio of power to volume reaches a maximum value of 2.3 when the stator yoke width 331a is 3.6 mm; when the stator yoke width 331a is 3.7 mm, the power to volume ratio is at the stator and rotor.
  • the outer diameter ratio is 0.62, the maximum value of 2.15 is reached.
  • Table 3 is the experimental data when the stator diameter is 46mm. When the motor is larger and the other parameters are the same, the power-to-volume ratio of the motor will be larger.
  • the ratio of the power to the volume of the motor is a value that reflects the power output efficiency of the motor. Under the same volume, the larger the ratio, the greater the motor power.
  • the power of the motor in Table 6 is the power value when the bare motor has a no-load speed of 20000 rpm.
  • the ratio of the stator and rotor outer diameters and the stator yoke width 331a all affect the ratio of motor power to volume.
  • the larger the stator and rotor outer diameter ratio is, the larger the rotor size is, and the stator yoke width 331a is correspondingly reduced; vice versa.
  • the larger the stator yoke width 331a the smaller the stator slot and the rotor size, and vice versa.
  • Reasonable design, rotor outer diameter ratio and yoke width can make the motor power reach a larger value.
  • the ratio of the motor power to the volume is selected to be greater than 2, so that the hand-held oscillating machine has a comfortable grip and a higher power under the same motor volume, especially the same stator diameter.
  • the stator yoke width 331a is increased or the rotor outer diameter ratio is increased, and the power of the motor exhibits an undulating change.
  • the stator to rotor outer diameter ratio ranges from 0.6 to 0.7 and the outer diameter of the stator is no greater than 50 mm.
  • the outer diameter of the stator is 40-50 mm.
  • the stator and rotor outer diameter ratios range from 0.6 to 0.65 and the yoke width ranges from 3.6 mm to 3.8 mm. The yoke width is excessively reduced to reduce the area of the slots, resulting in a reduction in stator winding.
  • the power of the motor fluctuates within a range close to the maximum.
  • the axial length of the motor that is, the length of the stator along the axial direction of the armature shaft is set to be not less than 40 mm, and the setting range is 45 mm to 60 mm, preferably 55 mm.
  • Table 8 shows that the stator has a diameter of 46 mm, the outer circumference of the grip is 198 mm, the axial length of the motor is 50 mm, and the bare motor idle speed is 20000 rpm (the idle speed when the motor is not mounted on the tool)
  • the values in Table 6 show the same motor volume, no-load speed and the outer circumference of the grip.
  • the stator yoke width 331a increases or the stator and rotor outer diameter ratios increase, and the power of the motor exhibits an undulating change.
  • the ratio of power to outer circumference reaches a maximum value of 0.81 when the stator yoke width 331a is 3.6 mm; when the stator yoke width 331a is 3.7 mm, the ratio of power to volume is determined.
  • the maximum value is 0.79.
  • the ratio of the power of the motor to the outer circumference of the grip is a value reflecting the power output efficiency of the motor. Under the same outer circumference, the larger the ratio, the larger the output power of the motor.
  • the ratio of the output power of the motor 3 to the peripheral circumference of the grip portion of the oscillating machine 600 is greater than 0.8 W/mm, where the output power is the maximum output power that the oscillating machine 600 inputs to the work object.
  • the outer circumference of the grip portion of the oscillating machine 600 is 150 mm to 200 mm. In order to have sufficient space inside the grip to accommodate the motor 3, the outer diameter of the stator is 40-50 mm.
  • the peripheral circumference of the grip portion of the oscillating machine 600 is set to 165 mm to 200 mm, and the outer diameter of the stator is 46-48 mm.
  • the ratio of the output power of the motor 3 to the peripheral circumference of the grip portion of the oscillating machine 600 is greater than 0.85 W/mm.
  • the peripheral circumference of the grip portion of the oscillating machine 600 is set to 180 mm, and the outer diameter of the stator 121 is 46 mm.
  • the ratio of the output power of the motor 3 to the peripheral circumference of the grip portion of the oscillating machine 600 is greater than 0.95 W/mm.
  • the bare metal idle speed of the above motor is 20,000 rpm, so it can be directly applied to the oscillating machine, so that the output shaft can meet the demand speed without any need for steady speed or other improvements.
  • the increase of the power of the motor will cause more heat during the operation of the motor.
  • the reduction of the diameter of the grip will reduce the area of the heat dissipating air passage.
  • the length of the lamination stack will lengthen the heat dissipating air passage. The above factors will cause the motor.
  • the number of air outlets can be increased, and a set of air outlets are additionally arranged at the bottom of the casing, so that the number of air outlets is three groups, and the discharge amount of hot air is increased, thereby improving the heat dissipation efficiency of the motor.
  • the number of air inlets can also be increased.
  • a set of air inlets is additionally provided at the bottom of the casing, so that the number of air inlets is three, and the amount of air entering the cold air is increased, thereby improving the heat dissipation efficiency of the motor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

Cette invention concerne un moteur à balais (3) et un outil électrique portatif mettant en œuvre le moteur (3). Le moteur (3) comprend : un stator monobloc (31) ; un rotor (32) disposé à l'intérieur du stator (31) ; et un arbre d'induit (33) solidarisé au rotor (32). Le diamètre extérieur du stator (31) n'est pas supérieur à 58 mm. La plage d'un rapport de diamètre extérieur du rotor au stator va de 0,6 à 0,7. Le rapport d'une puissance de sortie maximale du moteur (3) au volume de celui-ci est supérieur à 8,5 W/cm3. L'invention permet de configurer rationnellement un rapport de taille du stator au rotor dans le moteur, et d'améliorer la capacité de sortie du moteur (3) par comparaison avec des moteurs ayant la même taille. L'invention applique le moteur (3) à un outil électrique portatif pour améliorer sa puissance de sortie tout en assurant un confort de tenue de l'outil.
PCT/CN2018/115725 2016-05-31 2018-11-15 Moteur applicable à un outil électrique portatif, et outil électrique portatif WO2019096223A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US16/205,284 US11027405B2 (en) 2016-05-31 2018-11-30 Power tool

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN201721525916.4U CN207652226U (zh) 2017-11-15 2017-11-15 电动工具
CN201721525916.4 2017-11-15
CN201820258149 2018-02-13
CN201820258149.3 2018-02-13

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2017/086727 Continuation-In-Part WO2017206923A1 (fr) 2016-05-31 2017-05-31 Outil électrique oscillant

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US16/205,284 Continuation-In-Part US11027405B2 (en) 2016-05-31 2018-11-30 Power tool

Publications (1)

Publication Number Publication Date
WO2019096223A1 true WO2019096223A1 (fr) 2019-05-23

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PCT/CN2018/115725 WO2019096223A1 (fr) 2016-05-31 2018-11-15 Moteur applicable à un outil électrique portatif, et outil électrique portatif

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CN112222854A (zh) * 2020-09-30 2021-01-15 高那 一种手持式管道切割设备
EP4059662A1 (fr) * 2021-03-18 2022-09-21 X'Pole Precision Tools Inc. Machine-outil à meuler pour réduire la chaleur du boîtier
US11837935B2 (en) 2021-02-02 2023-12-05 Black & Decker, Inc. Canned brushless motor
EP4286097A1 (fr) * 2022-06-01 2023-12-06 X'Pole Precision Tools Inc. Meuleuse d'outils

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CN104853879A (zh) * 2012-12-20 2015-08-19 罗伯特·博世有限公司 具有电子换向的电动机和所集成的电子装置的手持式工具机
CN105305721A (zh) * 2014-05-30 2016-02-03 浙江绿动电机科技有限公司 冲击钻
CN205342073U (zh) * 2015-12-31 2016-06-29 苏州宝时得电动工具有限公司 电圆锯
CN106160390A (zh) * 2015-05-13 2016-11-23 株式会社牧田 电动工具

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CN102149515A (zh) * 2009-01-30 2011-08-10 日立工机株式会社 电动工具
CN104853879A (zh) * 2012-12-20 2015-08-19 罗伯特·博世有限公司 具有电子换向的电动机和所集成的电子装置的手持式工具机
CN105305721A (zh) * 2014-05-30 2016-02-03 浙江绿动电机科技有限公司 冲击钻
CN106160390A (zh) * 2015-05-13 2016-11-23 株式会社牧田 电动工具
CN205342073U (zh) * 2015-12-31 2016-06-29 苏州宝时得电动工具有限公司 电圆锯

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112222854A (zh) * 2020-09-30 2021-01-15 高那 一种手持式管道切割设备
US11837935B2 (en) 2021-02-02 2023-12-05 Black & Decker, Inc. Canned brushless motor
US11855521B2 (en) 2021-02-02 2023-12-26 Black & Decker, Inc. Brushless DC motor for a body-grip power tool
US11870316B2 (en) 2021-02-02 2024-01-09 Black & Decker, Inc. Brushless motor including a nested bearing bridge
US11876424B2 (en) 2021-02-02 2024-01-16 Black & Decker Inc. Compact brushless motor including in-line terminals
US11955863B2 (en) 2021-02-02 2024-04-09 Black & Decker Inc. Circuit board assembly for compact brushless motor
EP4059662A1 (fr) * 2021-03-18 2022-09-21 X'Pole Precision Tools Inc. Machine-outil à meuler pour réduire la chaleur du boîtier
EP4286097A1 (fr) * 2022-06-01 2023-12-06 X'Pole Precision Tools Inc. Meuleuse d'outils

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