JP4743666B2 - Electric tool - Google Patents

Description

  The present invention relates to an electric tool for cutting wood, steel, pipes, etc. in construction, equipment, renovation, demolition work, etc. of houses and buildings.

  There is a saver saw as a reciprocating type cutting tool (electric tool) driven by an electric motor. In a saver saw, generally, a reciprocating shaft (hereinafter referred to as a plunger) equipped with a linear saw blade (hereinafter referred to as a blade) is driven to reciprocate, and cutting is performed by the blade attached to the plunger.

  In the saver saw, a second shaft to which the rotation of the electric motor is transmitted is provided in order to reciprocate the plunger, and a reciprocating plate is provided between the second shaft and the plunger. The reciprocating plate converts the rotational movement of the second shaft into the reciprocating movement of the plunger.

More specifically, the second shaft is rotatably supported by the housing of the saver saw, and the second shaft is provided with an eccentric shaft. The reciprocating plate is connected to an eccentric shaft via a bearing, and the eccentric shaft is configured to rotate integrally with the second shaft. As a conventional example of a saver saw having such a configuration, there is JP-A-2002-79417.
JP 2002-79417 A

  In the conventional saver saw described above, further simplification of the configuration of the second shaft and the eccentric shaft is required, and an improvement in assemblability is required. Therefore, an object of the present invention is to provide an electric tool having a simpler configuration of a second shaft and an eccentric shaft and improved assemblability.

In order to solve the above-described problems, the present invention has a housing that houses a motor, a drive rotation shaft, and a radial projection that is formed integrally with the drive rotation shaft and projects in the radial direction of the drive rotation shaft. A drive shaft rotatably supported by the housing and driven to rotate by the motor; and a first motion converting means connected to the drive shaft and converting the rotational motion of the drive shaft into a reciprocating motion, The first motion conversion means has a first eccentric shaft that allows the drive rotation shaft to pass through the drive rotation shaft so as to be idle, and is spaced apart from the radial projection in the axial direction of the drive rotation shaft. A pinching member is provided on the drive rotation shaft, and the first eccentric shaft is driven by the pinching member and the radial projection in the axial direction of the drive rotation shaft. Providing power tools that can rotate together with the rotating shaft

  A clamping member is provided on the driving rotary shaft at a position spaced apart from the radial convex portion in the axial direction of the driving rotary shaft, and the first eccentric shaft is clamped in the axial direction of the driving rotary shaft by the clamping member and the radial convex portion. Thus, since the first eccentric shaft can be rotated integrally with the drive rotation shaft, the first eccentric shaft can be rotated integrally with the drive rotation shaft without directly fixing the first eccentric shaft to the drive rotation shaft. .

  In addition, since the radial convex portion is configured integrally with the drive rotation shaft, when manufacturing the drive shaft, the radial convex portion is manufactured separately from the drive rotation shaft and fixed to the drive rotation shaft. The process can be omitted. From these things, the structure of a 1st eccentric shaft and a drive rotating shaft can be simplified, manufacture can be made easy, and assemblability can be improved.

  Here, in the axial direction of the drive rotation shaft, the drive member extends between the sandwiching member and the radial protrusion at least in the axial direction of the drive rotation shaft with respect to the sandwiching member and the first eccentric shaft. It is preferable that an elastic body that exerts an urging force is provided.

  An elastic body is provided between the pinching member and the radial convex portion in the axial direction of the drive rotation shaft, and exerts a biasing force that expands in the axial direction of the drive rotation shaft with respect to at least the pinching member and the first eccentric shaft. Therefore, by pressing the first eccentric shaft against the radial convex portion, the first eccentric shaft, the radial convex portion, and the drive rotation shaft can be brought into an integral state that can rotate integrally.

  In addition, in the case where the clamping member is made of a nut and is screwed to one end of the drive rotating shaft, even if the screwing of the nut is loose, the female screw of the nut is driven by the urging force of the elastic body. By pressing against the male screw at one end of the rotating shaft, it is possible to prevent the nut from rotating and further loosening of the screw. Further, it is possible to prevent the nut from being overtightened when the electric tool is assembled.

  A gear for transmitting the rotation of the motor to the drive rotation shaft is coaxially fixed to the drive rotation shaft on the drive shaft, and the radial protrusion is formed between the gear and the first eccentric shaft. It is preferable to arrange | position between.

  A gear for transmitting the rotation of the motor to the drive rotation shaft is coaxially fixed to the drive rotation shaft on the drive shaft, and the radial convex portion is disposed between the gear and the first eccentric shaft. The radial convex portion serves as a spacer that separates a predetermined distance between the gear and the first eccentric shaft, so that the gear and the first eccentric shaft can be prevented from coming into contact with each other.

  Moreover, it is preferable that the width of the radial projection in the axial direction of the drive rotation shaft is a predetermined value that can avoid contact between the gear and the first eccentric shaft.

  Since the width of the radial convex portion in the axial direction of the drive rotation shaft is a predetermined value that can avoid contact between the gear and the first eccentric shaft, it is ensured that the gear and the first eccentric shaft contact each other. Can be prevented.

  A guide shaft extending in a reciprocating motion direction converted by the first motion conversion means and supported by the housing; and a guided portion that slides on the guide shaft, the guided portion being the guide The balance weight that reciprocates relative to the housing by sliding on the shaft, and the drive shaft and the balance weight are connected to each other, and the rotational motion of the drive shaft is converted by the first motion conversion means. A second motion converting means for converting the balance weight into a reciprocating motion in a direction opposite to the reciprocating motion and reciprocating the balance weight, and the second motion converting means has a second eccentric shaft that surrounds the drive rotation shaft. The second eccentric shaft is integrated with the drive rotation shaft by sandwiching the second eccentric shaft in the axial direction of the drive rotation shaft together with the first eccentric shaft by the clamping member and the radial convex portion. Rotate Door is preferable.

  The second motion converting means has a second eccentric shaft that surrounds the drive rotation shaft, and the second eccentric shaft is clamped in the axial direction of the drive rotation shaft together with the first eccentric shaft by the clamping member and the radial projection. Thus, the second eccentric shaft can be rotated integrally with the drive rotary shaft, so that the configuration of the first eccentric shaft, the second eccentric shaft, and the drive rotary shaft is simplified, the manufacture is facilitated, and the assemblability is improved. , Vibration due to reciprocation of the blanker and blade generated by the plunger and blade can be suppressed.

  Further, it is preferable that a plunger connected to the first motion converting means and having a blade attached to the tip thereof is provided, and the balance weight has a shape positioned on the outer periphery of the plunger.

Provided as a saver saw is an electric tool that exhibits the above-mentioned effects because the balance weight has a shape that is connected to the first motion conversion means and that can be fitted with a blade at the tip, and the balance weight has a shape located on the outer periphery of the plunger. it can.
The present invention also includes a motor having a rotating motor shaft, a second shaft rotated by the motor shaft, a first eccentric shaft through which the second shaft is inserted, and the second shaft integrally formed with the second shaft. A radial protrusion projecting in the radial direction, a first reciprocating plate attached to the first eccentric shaft, a plunger connected to the first reciprocating plate and reciprocating, and connected to and driven by the plunger A tip tool, and a clamping member attached to the second shaft and configured to clamp the first eccentric shaft in the second shaft in cooperation with the radial convex flange portion. When a force exceeding the force is applied, the electric power tool is configured such that the first eccentric shaft rotates idly with respect to the second shaft.
Here, the radial convex portion is formed of a flange portion, a bearing supported portion through which the second shaft is inserted, a bearing holding the bearing supported portion, a disc spring disposed in contact with the bearing, A nut disposed in contact with the disc spring, and the flange portion and the nut sandwich the first eccentric shaft, the bearing supported portion, and the disc spring, and the inner diameter of the bearing is It is preferable that it is larger than the outer diameter of the nut.

  ADVANTAGE OF THE INVENTION According to this invention, the structure of a 2nd shaft or an eccentric shaft is simpler, and the electric tool which improved the assembly property can be provided.

  A saver saw as an electric tool according to an embodiment of the present invention will be described with reference to FIGS. The saver saw 100 mainly includes a motor unit, a deceleration unit, a reciprocating shaft holding unit, a plunger rotation-reciprocation conversion unit, a balance weight holding unit, a balance weight rotation-reciprocation conversion unit, a blade holding unit, a main body front holding unit, And an oscillating cutting mechanism.

  (Motor part) The motor part has the electric motor 1 as FIG. 3 shows, and the electric motor 1 is incorporated in the motor housing 2 made of resin. The motor shaft 7 of the electric motor 1 extends to a speed reduction unit described later. A handle 3 is connected to the rear of the motor housing 2. The handle 3 has a built-in switch 4 for controlling power supply to the electric motor 1.

  (Deceleration part) The reduction part is arranged in front of the motor housing 2. A power transmission means described below is incorporated, and an aluminum inner cover 5 (FIG. 5) and a gear cover 6 (FIG. 4) connected to the front of the motor housing 2 are provided. A drive gear 8 is fixed to the tip of the motor shaft 7 so as to be rotatable together with the motor shaft 7. A second shaft 9 extending in parallel with the motor shaft 7 is provided in the speed reduction portion, and a driven gear 10 is coaxially attached to the second shaft 9 so as to be integrally rotatable with the second shaft 9. The electric motor 1 rotationally drives the second shaft 9 by the pair of reduction gears 8 and 10.

  As shown in FIG. 3 and the like, the second shaft 9 has an opposite phase with respect to the axis of the driven gear 10 so that a plunger 20 and a balance weight 31, which will be described later, can be reversed (movements whose phases are different by 180 °). A first eccentric shaft 9a and a second eccentric shaft 9b, which will be described later, each having a predetermined angle are provided. As shown in FIG. 13, the second shaft 9 has a drive rotation shaft 9 </ b> A and a flange portion 9 </ b> B configured integrally, and the longitudinal direction of the drive rotation shaft 9 </ b> A is oriented parallel to the motor shaft 7. A female screw (not shown) is threaded at one end thereof, and a nut 9C is screwed as shown in FIG.

  The flange portion 9B is provided in the vicinity of the other end of the drive rotating shaft 9A. The thickness of the flange portion 9B in the axial direction of the drive rotating shaft 9A is the same as that of the driven gear 10 that is press-fitted into a driven gear locking portion 9D described later. The predetermined value can avoid contact with a second eccentric shaft 9b described later. In the axial direction of the drive rotary shaft 9A, the flange portion 9B and the nut 9C are separated by a predetermined distance. A driven gear locking portion 9D for enlarging the diameter of the drive rotary shaft 9A and press-fitting the driven gear 10 closer to the other end of the drive rotary shaft 9A than the flange portion 9B is connected to the drive rotary shaft 9A and the flange portion 9B. It is provided as a unit. The other end portion 9E closer to the other end than the driven gear locking portion 9D is rotatably supported by the inner cover 5 via a bearing 9F as shown in FIG. The flange portion 9B corresponds to a radial convex portion, the nut 9C corresponds to a clamping member, and the driven gear 10 corresponds to a gear.

  A bearing supported portion 9c that is rotatably supported on the inner cover 5 via a bearing 9G is provided at a position on the drive rotation shaft 9A closer to the nut 9C than the first eccentric shaft 9a. The drive rotating shaft 9A is inserted through the bearing supported portion 9c. A disc spring 9d is provided in a portion closer to one end of the drive rotating shaft 9A than the bearing supported portion 9c. As shown in FIG. 14A, the disc spring 9d has a substantially disk shape in which a circular through hole 9e is formed at the center. When no force is applied to the disc spring 9d, the disc spring 9d protrudes in the axial direction of the disc spring 9d as shown in FIGS. 14 (b) and 14 (c) as it goes from the periphery to the center. ing.

  In a state in which a force is applied from the projecting direction of the disc spring 9d, that is, from the left direction to the right direction in FIG. 14B, the amount of projection of the disc spring 9d decreases, and the disc spring 9d has its axial direction, That is, an urging force acting on a second eccentric shaft 9b and a first eccentric shaft 9a, a bearing supported portion 9c, a disc spring 9d, and a nut 9C, which will be described later, is generated in an attempt to expand in the left-right direction in FIG. It is configured. As described above, the nut 9C (FIG. 3) is screwed into a portion closer to one end of the drive rotating shaft 9A than the disc spring 9d. As shown in FIG. 3, the disc shaft 9d has the second shaft 9 inserted through the through hole 9e.

  When viewed from the flange portion 9B side, a second eccentric shaft 9b and a first eccentric shaft 9a, which will be described later, a bearing supported portion 9c, and a disc spring 9d are inserted into the second shaft 9 in this order, and a nut is attached to one end of the second shaft 9 9C is screwed. As a result, the second eccentric shaft 9b and the first eccentric shaft 9a, which will be described later, are sandwiched between the nut 9C and the flange portion 9B with the disc spring 9d and the bearing supported portion 9c interposed in the axial direction of the drive rotary shaft 9A. To do. At this time, the disc spring 9d is not completely crushed between the nut 9C and the bearing supported portion 9c, and is in a state as shown in FIGS. 14 (b) and 14 (c). Yes. For this reason, the disc spring 9d can always exert the urging force that expands in the axial direction of the drive rotary shaft 9A. The disc spring 9d corresponds to an elastic body. Further, the motor housing 2, the inner cover 5, and the gear cover 6 constitute the housing of the present invention. The second shaft 9 corresponds to a drive shaft.

  Since the disc spring 9d as an elastic body is provided as described above, the first eccentric shaft 9a and the second eccentric shaft 9a are pressed by pressing a first eccentric shaft 9a and a second eccentric shaft 9b described later against the flange portion 9B. The eccentric shaft 9b, the flange portion 9B, and the drive rotation shaft 9A can be integrated with each other so as to be integrally rotatable.

  Further, even when the screwing of the nut 9C is loose, the nut 9C is prevented from rotating by pressing the nut 9C to the left in FIG. 3 by the urging force of the elastic body, and the nut 9C rotates. Thus, the screwing can be prevented from further loosening. Further, it is possible to prevent the nut 9C from being overtightened when the saver saw 100 is assembled.

  With the above-described configuration, the first eccentric shaft 9a and the second eccentric shaft 9b can be integrally rotated with the drive rotary shaft 9A without directly fixing the first eccentric shaft 9a and the second eccentric shaft 9b, which will be described later, to the drive rotary shaft 9A. It can be. Further, since the flange portion 9B is configured integrally with the drive rotating shaft 9A, a complicated process of manufacturing the flange portion 9B separately and fixing the flange portion 9B to the drive rotating shaft 9A can be omitted. Therefore, the configuration of the first eccentric shaft 9a, the second eccentric shaft 9b, and the drive rotary shaft 9A can be simplified, the manufacturing can be facilitated, and the assemblability can be improved. Moreover, since the balance weight 31 is provided in such a saver saw, it is possible to suppress vibrations caused by reciprocating movements of the flanger 20 and the blade 27 generated by the plunger 20 and the blade 27 which will be described later.

  Further, since the flange portion 9B is disposed between the driven gear 10 and the first eccentric shaft 9a, the flange portion 9B becomes a spacer that separates a predetermined interval between the driven gear 10 and the first eccentric shaft 9a. It can prevent that the driven gear 10 and the 1st eccentric shaft 9a contact | abut. In addition, the width of the flange portion 9B in the axial direction of the drive rotating shaft 9A is a predetermined value that can avoid contact between the driven gear 10 and a second eccentric shaft 9b described later. It can prevent reliably that the eccentric shaft 9b contact | abuts.

  (Reciprocating shaft holding portion) Two shaft bolts 12 are attached to the front of the gear cover 6 as shown in FIG. 4 and the like, and a guide sleeve 13 is attached to the tip end portion of the shaft bolt 12. It is attached so that it can swing around. Here, a slight gap is actually formed between the inner peripheral surface of the gear cover 6 and the outer peripheral surface of the guide sleeve 13, and the guide sleeve 13 is connected to the shaft bolt as described above within this gap. It can swing around 12 axes. In FIG. 4, this gap does not appear. A rectangular through hole 14 is formed at the rear end of the guide sleeve 13 on the electric motor 1 side as shown in FIGS. 3 and 5, and the change is attached so as to be rotatable through the inner cover 5. The shaft 15 passes through the rectangular through hole 14 of the guide sleeve 13.

  As shown in FIG. 5, a concave portion is formed in the central portion of the change shaft 15 as if a pair of guide shafts 15 were cut out symmetrically in the diameter direction about the shaft center. The portion of the change shaft 15 to be formed is a pair of symmetrical flat portions 15a and 15a. By rotating the change shaft 15 with the change lever 16, the swing of the guide sleeve 13 can be selectively allowed or inhibited. FIG. 5 shows a state where the swing of the guide sleeve 13 is allowed. Accordingly, the swing of the plunger 20 supported inside the guide sleeve 13 through the bearing metal 19 can be selectively allowed or suppressed.

  (Plunger rotation-reciprocation conversion portion) As shown in FIGS. 3, 11, and 12, the second shaft 9 is provided with a first eccentric shaft 9a so as to surround the periphery thereof. A through hole 9f is formed in the first eccentric shaft 9a, and the second shaft 9 is inserted through the through hole 9f. When the second shaft 9 does not pass through the through-hole 9f and the first eccentric shaft 9a is not clamped in the axial direction of the second shaft 9 by a flange portion 9B and a nut 9C described later, the second shaft 9, the first eccentric shaft 9a can rotate. The first eccentric shaft 9a has a first inclined shaft portion 9H, and the first eccentric shaft 9a has an oscillating shaft portion 18a via two bearings 17 in contact with the first inclined shaft portion 9H. A first reciprocating plate 18 is attached. A spherical portion 18b is provided at the tip of the swing shaft portion 18a.

  A bearing metal 19 is press-fitted into the front inside of the guide sleeve 13, and a plunger 20 is attached so as to reciprocate through the bearing metal 19. A large-diameter portion 20a that slides with a slight gap is provided on the inner periphery of the guide sleeve 13 behind the plunger 20, and a hole portion 20b is provided in the large-diameter portion 20a at a right angle to the axial direction. The swinging shaft portion 18a of the first reciprocating plate 18 penetrates the plunger 20 and the spherical portion 18b at the tip is engaged with the inside of the hole portion 20b so as to be able to roll with a slight clearance, and the rotation of the second shaft 9 The movement is converted into a reciprocating movement of the plunger 20. The first eccentric shaft 9a and the first reciprocating plate 18 correspond to first motion converting means.

(Balance weight holder)
The inner cover 5 and the gear cover 6 support two guide shafts 33 (FIG. 6) that are arranged in parallel and extend in a reciprocating direction of a plunger described later. One end of each of the two guide shafts 33 is fixed and supported by the inner cover 5, and the other end is fixed and supported by the gear cover 6. The two guide shafts 33 guide the balance weight 31.

  As shown in FIG. 8, the balance weight 31 has a substantially bowl-like shape having an opening on the lower side, includes the guide sleeve 13 (FIG. 6, etc.), and its center of gravity substantially coincides with the center of gravity of the plunger 20. It has a cross-sectional shape. A pair of lower end portions in FIG. 8A that define the opening form a guided portion 31A. A guide shaft through hole 31d is formed in the guided portion 31A, and the guide shaft 33 passes through the guide shaft through hole 31d. With this configuration, the balance weight 31 is supported by the two guide shafts 33 so as to reciprocate in the reciprocating direction of the plunger 20. The guide shaft through hole 31d corresponds to a guide shaft insertion space.

  As shown in FIG. 8A, a connecting recess 31e that is recessed substantially upward in FIG. 8A is formed in the vicinity of the guide shaft through hole 31d formed in one of the pair of guided portions 31A. Has been. The portion of the balance weight 31 in which the connecting recess 31e is formed forms a connecting portion 31B. As shown in FIG. 9A, the connecting recess 31e is engaged with a spherical portion 32b of a second reciprocating plate 32, which will be described later, so that it can roll with a slight gap. The connecting recess 31e and the guide shaft through hole 31d are in communication with each other, and the lubricant can flow back and forth between the guide shaft through hole 31d and the connecting recess 31e.

  For this reason, the lubricant can be constantly supplied into the guide shaft through hole 31d and the connecting recess 31e. Further, since the connecting recess 31e is formed in the vicinity of the guide shaft 33 formed on one of the pair of guided portions 31A, the balance weight is prevented from being tilted with respect to the guide shaft and causing galling. Can do. For this reason, the balance weight can be smoothly slid with respect to the guide shaft.

  A groove 31f is formed on the inner peripheral surface of the balance weight 31 that defines the guide shaft through hole 31d. A total of eight grooves 31f are formed in each guide shaft through hole 31d. Four grooves 31f are formed at equal intervals in the circumferential direction in one guide shaft through hole 31d, and are formed from one end to the other end of the guide shaft through hole 31d. Of the four grooves 31f of the one guide shaft through hole 31d in FIG. 8A, the groove 31f located at the lowermost position communicates directly with the connecting recess 31e as shown in FIGS. ing.

  Therefore, the lubricant can flow back and forth in the groove 31f and the connecting recess 31e, and the state where the lubricant is supplied without deviation in the guide shaft through hole 31d can be maintained. Further, since the groove 31f communicates directly with the connection recess 31e, the lubricant in the connection recess 31e can be easily flowed into the groove 31f, and the lubricant in the groove 31f can enter the connection recess 31e. It can be easily introduced.

  (Balance Weight Rotation-Reciprocation Conversion Unit) As shown in FIGS. 3, 11, and 12, the second shaft 9 is provided with a second eccentric shaft 9b so as to surround the periphery thereof. . The second eccentric shaft 9b is formed integrally with the first eccentric shaft 9a and has a through hole 9g. The second shaft 9 is inserted through the through hole 9g. When the second shaft 9 does not pass through the through hole 9g and the second eccentric shaft 9b is not sandwiched between the flange portion 9B and the nut 9C in the axial direction of the second shaft 9, Thus, the second eccentric shaft 9b is rotatable. The second eccentric shaft 9b has a second inclined shaft portion 9I, and the second eccentric shaft 9b has two bearings 17 in contact with the second inclined shaft portion 9I. A second reciprocating plate 32 having a swing shaft portion 32a is attached. A spherical portion 32b is formed at the tip of the swing shaft portion 32a.

  The first reciprocating plate 18 and the second reciprocating plate 32 are attached to the second shaft 9 at an offset angle α ° as shown in FIG. 6 so that the spherical portions 18b and 32b do not interfere with each other. The inclination angle of the first inclined shaft portion 9H and the second inclined shaft portion 9I of the second shaft 9 is set to an offset angle α ° so that the plunger 20 and the balance weight 31 can be reversed (movements whose phases are different by 180 °). It is decided in consideration.

  That is, each inclination angle with respect to the axis of the driven gear 10 is set to be maximum at the offset angle α °. The second eccentric shaft 9b and the second reciprocating plate convert the rotational motion of the second shaft 9 into the reciprocating motion of the balance weight 31, and correspond to second motion converting means.

  In order to substantially eliminate the vibration of the plunger 20 in the axial direction, the product of the mass of the balance weight 31 and the amount of reciprocating motion (hereinafter referred to as balance weight stroke amount) is the product of the mass of the plunger 20 and the amount of reciprocating motion (hereinafter referred to as plunger stroke amount). Achieved by making it equal to the product.

  (Blade holding part) As shown in FIG. 3 and the like, the blade mounting end 20c in front of the plunger 20 is provided with a slit 20d for inserting the blade 27 and a stepped blade locking pin 30. Blade holders 28 and 29 are provided so as to enclose the outer periphery of the portion 20c. The blade 27 can be mounted by rotating the blade holder 28 backward to move the stepped blade locking pin 30 to the open position so that the blade 27 can be inserted into the slit 20d, and the blade holder 28 is rotated forward in the opposite direction. Thus, the stepped blade locking pin 30 engages with the blade 27 and the blade 27 is fixed. Further, as will be described later, the blade 27 can be mounted upside down. The configuration of the blade holding portion is described in the application (Japanese Patent Application No. 11-242508) filed by the present applicant.

  (Main body front holding portion) As shown in FIG. 4, a resin front cover 24 is provided outside the inner cover 5, the gear cover 6, and a part of the housing 1. As shown in FIG. A base 25 for stabilizing the saver saw 100 against the material to be cut 36 at the time of cutting work is attached to the front end portion of the gear cover 6 by a fixing lever 26 so as to be able to advance and retract.

  (Oscillating cutting mechanism portion) The guide sleeve 13 is formed with an elongated hole portion 13a (FIG. 6) extending in the axial direction thereof. A roller shaft 21 passes through the long hole portion 13a and the plunger 20. Swing rollers 22 are rotatably attached to both ends of a roller shaft 21 that penetrates the elongated hole portion 13a and the plunger 20, and the roller shaft 21 and the swing roller 22 reciprocate integrally with the plunger 20 using the elongated hole portion 13a as a guide. It is provided for exercise. The height of the elongated hole portion 13a is slightly larger than the shaft diameter of the roller shaft 21, and the circumferential rotation of the plunger 20 is suppressed by the guide sleeve 13 via the roller shaft 21, and the blade 27 is prevented from falling. I try to prevent it.

  At the top and bottom of the swing roller 22, as shown in FIG. 7, raceway surfaces 31 a and 31 b having a length longer than the sum of the plunger stroke amount and the balance weight stroke amount in the axial direction of the plunger 20 Are formed as part of a pair of long groove shapes. The raceway surfaces 31 a and 31 b have a slight inclination angle in order to adjust the swinging momentum of the plunger 20.

  As shown in FIGS. 10, 12, and 15, when the change shaft 15 allows the guide sleeve 13 to swing and the plunger 20 is swingable, the guide sleeve 13 can be Oscillating motion is possible in a range where 22 contacts the track surface 31a or 31b. That is, the balance weight 31 has a role of eliminating the vibration in the axial direction of the plunger 20 and a role of supporting the swinging motion of the guide sleeve 13 including the plunger 20.

  As shown in FIG. 15, the guide sleeve 13 is set to swing up and down within a range of about 1.54 °, but is indirectly engaged through the balance weight 31 and the swing roller 22. Therefore, there is no direct interference. FIG. 15 shows a state where the rear portion of the guide sleeve 13 swings upward (solid line) or downward (broken line), and the guide sleeve 13 contacts the balance weight 31 in any state, that is, interferes. It shows no.

  (Explanation of cutting operation by linear reciprocating motion) As shown in FIGS. 16 to 18, the change shaft 15 is shown in FIG. 1 when the swinging motion of the guide sleeve 13 is suppressed. In this way, the pressing force F1 is applied by the operator during the cutting operation for cutting the material to be cut 36, but the swinging motion of the guide sleeve 13 is suppressed. There is no contact with the 31 raceway surface 31a or 31b. Therefore, the blade 27 performs a simple linear reciprocating motion as indicated by arrows in the figure. Such a cutting form by a simple linear reciprocating motion is suitable for cutting a hard material having a large cutting reaction force such as a steel material.

  (Description of Orbital Cutting Operation when Blade is Mounted Downward) As shown in FIGS. 19 to 21, the change shaft 15 releases the swinging motion of the guide sleeve 13, and the blade 27 is mounted downward to perform orbital cutting. When the cutting work for cutting the material to be cut 36 is performed as shown in FIG. 1, the operator applies a pressing force F <b> 1 to the blade 27. Then, the plunger 20 pushes down the rear end portion of the guide sleeve 13 about the shaft center of the shaft bolt 12 via the blade 27.

  As a result, the swing roller 22 is pressed against the raceway surface 31a of the balance weight 31 and reciprocates while rolling, so that the guide sleeve 13 is set to 0.44 ° to 1.. Perform reciprocating motion while swinging at an angle of 54 °. As a result, the blade 27 draws an arc-shaped locus as indicated by an arrow in the figure and performs orbital cutting. During this time, the balance weight 31 is reciprocating in a phase opposite to that of the plunger 20, and substantially eliminates vibration in the axial direction of the plunger 20.

  (Description of Orbital Cutting Operation when Blade is Mounted Upward) As shown in FIGS. 22 to 24, the change shaft 15 releases the swinging motion of the guide sleeve 13, and the blade 27 is mounted upward. When the orbital cutting is performed by inverting the saver saw body as shown in FIG. 2, a pressing force F2 is applied by the operator during the cutting operation. Then, the plunger 20 pushes up the rear end portion of the guide sleeve 13 through the blade 27 about the axis of the shaft bolt 12 in the direction opposite to that shown in FIGS.

  As a result, the swing roller 22 is pressed against the raceway surface 31b of the balance weight 31 and reciprocates while rolling, so that the guide sleeve 13 swings at an angle of 0.44 ° to 1.54 ° as shown in the figure. The reciprocating motion is performed while moving, and as a result, the blade 27 draws an arc-shaped locus as indicated by an arrow in the figure, and orbital cutting is performed. Also during this time, the balance weight 31 reciprocates in the opposite phase to the plunger 20 and substantially eliminates the vibration of the plunger 20 in the axial direction.

  When the balance weight 31 is reciprocated in the above three states of FIGS. 16 to 18, 19 to 21, and 22 to 24, the balance weight 31 is prevented from being inclined with respect to the reciprocating direction. Smooth reciprocation without galling occurs.

  In addition, the second shaft 9 that rotates when the rotation of the electric motor 1 is transmitted during the reciprocating motion of the blanker 20 and the blade 27 in the three states of FIGS. 16 to 18, 19 to 21, and 22 to 24, The nut 9C and the flange portion 9B rotate integrally with the first eccentric shaft 9a and the second eccentric shaft 9b sandwiched between the bearing supported portion 9c and the disc spring 9d. However, the integral rotation is performed when the blade 27 is pressed against the workpiece with a predetermined force or less. When pressed by a force exceeding the predetermined force, the first eccentric shaft 9a and the second eccentric shaft 9b rotate idly with respect to the second shaft 9 against the urging force of the disc spring 9d. This prevents the electric motor 1 from being damaged.

  The power tool of the present invention is not limited to the above-described embodiment, and various modifications and improvements can be made within the scope described in the claims. For example, in the present embodiment, the second shaft 9b, the first eccentric shaft 9a, the bearing supported portion 9c, and the disc spring 9d are inserted into the second shaft 9 from the flange portion 9B side in this order. The nut 9C is screwed to one end of the second eccentric shaft 9b, with the nut 9C and the flange portion 9B interposing the disc spring 9d and the bearing supported portion 9c in the axial direction of the drive rotating shaft 9A. Although the first eccentric shaft 9a is clamped, it does not have to be inserted and clamped in this order. For example, instead of disposing the driven gear 10 on the side opposite to the second eccentric shaft 9b with respect to the flange portion 9B in the axial direction of the drive rotating shaft 9A as in the present embodiment, the driven gear is used as the second eccentric shaft 9b and the second eccentric shaft 9b. As a configuration that is inserted through the second shaft together with the one eccentric shaft 9a, the bearing supported portion 9c, and the disc spring 9d, these may be sandwiched between the flange portion 9B and the nut 9C.

  In the present embodiment, the disc spring 9d is used, but the disc spring 9d is not limited thereto. For example, a spring may be used. Further, a washer may be used instead of the elastic body such as the disc spring 9d.

  In this embodiment, the balance weight and the second motion conversion means are provided, but these may not be provided. Further, the thickness of the flange portion 9B in the axial direction of the drive rotating shaft 9A is not limited to the thickness of the flange portion 9B in the present embodiment. For example, when the second eccentric shaft 9b constituting the second motion converting means is not provided, the flange portion is thickened by that amount so that the first eccentric shaft and the driven gear are sufficiently separated from each other. Avoid contact with the driven gear.

  Further, in the description of the above embodiment, a mode related to an electric tool called a saver saw that is connected to the first motion conversion means and includes a plunger that can be fitted with a blade at the tip has been described. However, the embodiment is not limited to the saver saw. For example, a power tool called a hammer or hammer drill having a configuration in which the first motion conversion means includes a reciprocating piston and a striker that reciprocates due to the reciprocating motion of the piston and strikes the tip tool. Even if the present invention is applied, the same effects can be obtained.

The side view which shows a mode that the process member is cut | disconnected with the saver saw which is an electric tool by embodiment of this invention. The side view which shows a mode that the process member is cut | disconnected with the saver saw which is an electric tool by embodiment of this invention. The partial cross section side view which shows the saver saw which is an electric tool by embodiment of this invention. FIG. 4 is a cross-sectional view taken along line IV-IV in FIG. 3. Sectional drawing along the VV line of FIG. Sectional drawing along the VI-VI line of FIG. Sectional drawing along the VII-VII line of FIG. It is a figure which shows the balance weight of the saver saw which is an electric tool by embodiment of this invention, (a) is principal part sectional drawing, (b) is an enlarged view in the circle of (a). It is a figure which shows the balance weight of the saver saw which is an electric tool by embodiment of this invention, (a) is principal part sectional drawing, (b) is an enlarged view in the circle of (a). The principal part sectional view showing the state where the saver saw which is an electric tool by an embodiment of the invention is operating. The principal part sectional view showing the state where the saver saw which is an electric tool by an embodiment of the invention is operating. The principal part sectional view showing the state where the saver saw which is an electric tool by an embodiment of the invention is operating. The principal part sectional drawing which shows the second shaft of the saver saw which is an electric tool by embodiment of this invention. It is a figure which shows the disk spring of the saver saw which is an electric tool by embodiment of this invention, (a) is a front view, (b) is a side view, (c) is side sectional drawing. The conceptual diagram for demonstrating the orbital cutting locus in the saver saw which is an electric tool by embodiment of this invention. The conceptual diagram which shows the linear cutting locus in the saver saw which is an electric tool by embodiment of this invention, and shows the state which the braid | blade protrudes most forward. The conceptual diagram which shows the state which shows the linear cutting locus in the saver saw which is an electric tool by embodiment of this invention, and has a braid | blade in the approximate center position of reciprocation. The conceptual diagram which shows the linear cutting locus in the saver saw which is an electric tool by embodiment of this invention, and shows the state which the braid | blade protrudes most back. The conceptual diagram which shows the orbital cutting locus | trajectory in the saver saw which is an electric tool by embodiment of this invention, and shows the state which the braid | blade protrudes most forward. The conceptual diagram which shows the orbital cutting locus in the saver saw which is an electric tool by embodiment of this invention, and shows the state which has a braid | blade in the approximate center position of reciprocation. The conceptual diagram which shows the orbital cutting locus in the saver saw which is an electric tool by embodiment of this invention, and shows the state which the braid | blade protrudes most back. The conceptual diagram which shows the orbital cutting locus | trajectory in the saver saw which is an electric tool by embodiment of this invention, and shows the state which the braid | blade protrudes most forward. The conceptual diagram which shows the orbital cutting locus in the saver saw which is an electric tool by embodiment of this invention, and shows the state which has a braid | blade in the approximate center position of reciprocation. The conceptual diagram which shows the orbital cutting locus in the saver saw which is an electric tool by embodiment of this invention, and shows the state which the braid | blade protrudes most back.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Electric motor 2 ... Housing 9 ... Second shaft 9B ... Flange part 9C ... Nut 9a ... 1st eccentric shaft 9b ... 2nd eccentric shaft 9d ... Disc spring DESCRIPTION OF SYMBOLS 10 ... Driven gear 18 ... 1st reciprocating plate 20 ... Plunger 27 ... Blade 31 ... Balance weight 31A ... Guided part 31d ... Guide shaft through-hole 31e ... Connection Recessed part 31f ... Groove 32 ... Second reciprocating plate 33 ... Guide shaft

Claims (8)

A housing for housing the motor;
A drive rotary shaft, a drive shaft configured integrally with the drive rotary shaft and having a radial projection protruding in the radial direction of the drive rotary shaft, rotatably supported by the housing, and driven to rotate by the motor The axis,
A first motion converting means coupled to the drive shaft and converting the rotational motion of the drive shaft into a reciprocating motion;
The first motion conversion means has a first eccentric shaft that allows the drive rotation shaft to pass through the drive rotation shaft so as to be idle .
A clamping member is provided on the driving rotary shaft at a position spaced apart from the radial convex portion in the axial direction of the driving rotary shaft, and the first eccentric shaft is driven to rotate by the clamping member and the radial convex portion. An electric power tool characterized in that the first eccentric shaft can be rotated integrally with the drive rotation shaft by being sandwiched in the axial direction of the shaft.   In the axial direction of the drive rotation shaft, an urging force that expands in the axial direction of the drive rotation shaft with respect to at least the sandwiching member and the first eccentric shaft is provided between the sandwiching member and the radial protrusion. The power tool according to claim 1, further comprising an elastic body that acts.   A gear for transmitting the rotation of the motor to the drive rotation shaft is coaxially fixed to the drive rotation shaft on the drive shaft, and the radial protrusion is between the gear and the first eccentric shaft. The power tool according to claim 1, wherein the power tool is arranged.   4. The electric motor according to claim 3, wherein a width of the radial convex portion in the axial direction of the drive rotating shaft is a predetermined value capable of avoiding contact between the gear and the first eccentric shaft. tool. A guide shaft extending in a reciprocating motion direction converted by the first motion converting means and supported by the housing;
A balance weight having a guided portion that slides on the guide shaft, and the guided portion reciprocates relative to the housing by sliding on the guide shaft;
The drive shaft and the balance weight are connected to each other, and the rotational motion of the drive shaft is converted into a reciprocal motion in a direction opposite to the reciprocal motion converted by the first motion conversion means, and the balance weight is reciprocated. Second motion conversion means,
The second motion converting means has a second eccentric shaft that wraps around the drive rotation shaft, and the second eccentric shaft is connected to the drive rotation shaft together with the first eccentric shaft by the clamping member and the radial convex portion. 5. The electric power tool according to claim 1, wherein the second eccentric shaft can be integrally rotated with the drive rotation shaft by being sandwiched in the axial direction. A plunger connected to the first motion converting means and capable of attaching a blade to the tip;
The electric power tool according to any one of claims 1 to 5, wherein the balance weight has a shape located on an outer periphery of the plunger.   A motor having a rotating motor shaft;
  A second shaft rotated by the motor shaft;
  A first eccentric shaft through which the second shaft is inserted;
  A radial protrusion that is configured integrally with the second shaft and protrudes in the radial direction of the second shaft;
  A first reciprocating plate attached to the first eccentric shaft;
  A reciprocating plunger connected to the first reciprocating plate;
  A tip tool connected to and driven by the plunger;
  A clamping member attached to the second shaft and for clamping the first eccentric shaft in the second shaft in cooperation with the radial convex flange portion;
  An electric tool characterized in that the first eccentric shaft is idled with respect to the second shaft when a force exceeding a predetermined force is applied to the tip tool.   The radial convex portion comprises a flange portion,
  A bearing supported portion through which the second shaft is inserted;
  A bearing for holding the bearing supported portion;
  A disc spring disposed in contact with the bearing;
  A nut disposed in contact with the disc spring;
  The first eccentric shaft, the bearing supported portion, and the disc spring are clamped by the flange portion and the nut, and the inner diameter of the bearing is larger than the outer diameter of the nut. The electric tool described.

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