CN215392887U

CN215392887U - Reciprocating saw

Info

Publication number: CN215392887U
Application number: CN202121127041.9U
Authority: CN
Inventors: 戴伟
Original assignee: Nanjing Jiuchi Electromechanical Industry Co ltd
Current assignee: Nanjing Jiuchi Electromechanical Industry Co ltd
Priority date: 2021-05-25
Filing date: 2021-05-25
Publication date: 2022-01-04
Anticipated expiration: 2031-05-25

Abstract

The utility model relates to a reciprocating saw, and belongs to the technical field of electric tools. This reciprocating saw, including one end for holding the position, the other end settles actuating mechanism's casing, its characterized in that: the motor output shaft of the driving mechanism is in transmission connection with a crankshaft, two ends of which are respectively supported in the shell, through a rotary transmission mechanism, a first eccentric wheel forming a rotary moving pair with a chute at the inner end of the reciprocating rod and a second eccentric wheel forming a rotary moving pair with a balancing weight are arranged between two supporting ends of the crankshaft, and the circumferential phases of the first eccentric wheel and the second eccentric wheel are opposite; the reciprocating rod and the balancing weight and the shell respectively form a moving pair moving in opposite directions. The two ends of the crankshaft are supported, so that compared with a cantilever structure, the crankshaft structure is very stable and reliable in support and is more beneficial to shock absorption.

Description

Reciprocating saw

Technical Field

The utility model relates to a reciprocating saw, in particular to an electric reciprocating saw, and belongs to the technical field of electric tools.

Background

A reciprocating saw is a commonly used electric tool for cutting a workpiece by driving a saw blade to reciprocate, and is disclosed in european patent publication No. EP3757427a1, which discloses an electrically driven reciprocating tool including a motor, a reciprocating mechanism, and a planetary gear assembly; the reciprocating mechanism converts the rotary power generated by the motor into reciprocating linear motion of the saw blade. Since the conventional reciprocating mechanism is an unbalanced mechanism, the reciprocating saw operates with a large vibration. To this end, chinese patent application No. 201910110183.5 discloses a reciprocating saw having an effect of suppressing vibration by designing a balance weight having a phase opposite to that of a reciprocating mechanism in addition to a basic structure. However, the balance weight and the driving rotating shaft of the reciprocating motion driving eccentric wheel are both cantilever structures supported by one end, so that the stability and the stationarity are poor, and the effect of inhibiting vibration is adversely affected. Although it is known that the cantilever structure with single end support is far less stable and reliable than the simple support structure with double end support, the cantilever support is adopted, and the open end is convenient for assembly because the reciprocating motion and balance weight mechanism has a plurality of rotating moving pair components which need to be sleeved on the driving rotating shaft. The simple support structure with double-end support can be difficult or even impossible to assemble the complete assembly.

SUMMERY OF THE UTILITY MODEL

The utility model aims to: aiming at the defects in the prior art, the balance block and the eccentric driving rotating shaft support structure are stable, the reciprocating saw is convenient to assemble and compact in structure, the damping performance is further effectively improved, and the reciprocating saw is more convenient to operate.

In order to achieve the above object, the reciprocating saw of the present invention comprises: one end is a holding part, the other end is provided with a shell of a driving mechanism, a motor output shaft of the driving mechanism is in transmission connection with a crankshaft, the two ends of the crankshaft are respectively supported in the shell, a first eccentric wheel forming a rotary moving pair with a chute at the inner end of a reciprocating rod and a second eccentric wheel forming a rotary moving pair with a balancing weight are arranged between the two supporting ends of the crankshaft, and the circumferential phases of the first eccentric wheel and the second eccentric wheel are opposite; the reciprocating rod and the balancing weight and the shell respectively form a moving pair moving in opposite directions.

Because the two ends of the crankshaft are supported, compared with a cantilever structure, the crankshaft structure has the advantages of very stable and reliable support and is more beneficial to shock absorption.

The crankshaft is of an integral structure, and the distance between two ends of the sliding groove at the inner end of the reciprocating rod is greater than or equal to the sum of the center distance between the first eccentric wheel and the second eccentric wheel and the radius of the first eccentric wheel and the radius of the second eccentric wheel. The structure is compact due to the reasonable design of the structural size of the crankshaft eccentric wheel and the reciprocating rod sliding groove, and the interference can be avoided only by properly mastering the mutual positions of the crankshaft and the reciprocating rod during assembly, so that the two eccentric wheels can pass through the inner end sliding grooves as required, and the assembly process can be as convenient as a cantilever structure.

Further, the sum of the radius of the end cylindrical section of the crankshaft and the eccentricity of the first eccentric wheel is larger than the radius of the first eccentric wheel.

And furthermore, the diameters of the first eccentric wheel and the second eccentric wheel are equal, two ends of the inner sliding groove of the reciprocating rod are arc-shaped, and the distance between the arcs at the two ends of the inner sliding groove is more than or equal to the sum of the center distance of the two eccentric wheels and the diameter of the eccentric wheels.

The utility model has another further perfection that the crankshaft is formed by combining crank throw fulcrum shafts at two ends and a crank throw pin shaft in the middle, the crank throw fulcrum shaft is formed by a support shaft head and a crank throw with an eccentric hole, the crank throw pin shaft is formed by pin shafts extending reversely from two ends of a middle spacer and a middle spacer, and the two pin shafts are respectively sleeved as a movable fit pin shaft sleeve of the first eccentric shaft and the second eccentric shaft and are pressed into the corresponding eccentric hole; the outer diameter of the pin shaft sleeve is larger than or equal to the width of the crank throw and the middle spacer. The crankshaft is combined in sections, so that the structure is compact as far as possible even if the eccentricity is large, and the interference can be avoided only by properly mastering the press mounting step of the crankshaft during assembly, so that the two eccentric shafts respectively form corresponding rotary moving pairs with the inner end sliding grooves of the reciprocating rods and the balancing weights, the assembly process is simple, especially the original sliding friction of the rotary moving pairs is changed into rolling friction by the pin shaft sliding sleeves, and the relative motion is light and smooth.

Furthermore, the crank pin shaft is formed by pressing and mounting oppositely extending pin shafts through two eccentric holes of the middle spacer and the middle spacer, and the two pin shafts are respectively sleeved with a movable fit pin shaft sleeve serving as a first eccentric shaft and a second eccentric shaft.

Still further, the crank fulcrum shaft is composed of a supporting shaft head and a connected crank which symmetrically extends towards two sides from the end part of the supporting shaft head.

The utility model is further perfected in that a gear box is fixedly arranged at the position of the shell, which is adjacent to the output shaft, and the gear box is provided with an upper end concave embedded with an upper bearing; the gear box is fixedly connected with the counterweight box, and the counterweight box is provided with a lower end concave embedded with a lower bearing.

The utility model is further perfected in that two ends of the inner sliding groove of the reciprocating rod are arc-shaped, a sliding insertion piece extends from one side of the periphery of the sliding groove, the other side of the sliding groove is fixedly connected with a cylindrical section, the sliding insertion piece is matched with an insertion hole of a rear sliding sleeve fixedly connected with a gear box to form a moving pair, and the cylindrical section is matched with a through hole of a front sliding sleeve fixedly connected with the gear box to form a moving pair.

Drawings

The utility model will be further described with reference to the accompanying drawings.

Fig. 1 is a schematic structural diagram of a first embodiment of the present invention.

FIG. 2 is a schematic diagram of a balance block and an eccentric driving portion of the embodiment shown in FIG. 1.

Fig. 3 is a bottom view of fig. 2.

Fig. 4 is a schematic perspective exploded view of a driving mechanism portion of the embodiment of fig. 1.

Fig. 5 is a schematic structural diagram of a second embodiment of the present invention.

FIG. 6 is a schematic view of the balance block and the eccentric driving portion of the embodiment of FIG. 5.

Fig. 7 is a bottom view of fig. 6.

Fig. 8 is a schematic perspective view of fig. 7.

Fig. 9 is a perspective exploded view of the crankshaft assembly of fig. 8.

Fig. 10 is a schematic perspective exploded view of the driving portion of the embodiment of fig. 5.

Detailed Description

Example one

As shown in fig. 1 to 4, one end of the housing 1 is a holding portion 1-1, and the other end is provided with a driving mechanism 2. An output shaft 2-2 of a motor 2-1 of the driving mechanism 2 is in transmission connection with a crankshaft 4, two ends of which are respectively supported between an upper bearing 4-1 and a lower bearing 4-2 in a gear box 5 and a counterweight box 6 through a rotary transmission mechanism. Specifically, a gear box 5 is fixedly arranged at the position, close to an output shaft 2-2, of the shell 1, the gear box 5 is provided with an upper end concave 5-1 embedded with an upper bearing 4-1, the gear box 5 is fixedly connected with a counterweight box 6, and the counterweight box 6 is provided with a lower end concave 6-1 embedded with a lower bearing 4-2.

The rotary transmission mechanism comprises a small gear 2-3 coaxial with the output shaft 2-2 and a large gear 4-3 coaxial with the supporting end of the crankshaft 4 and meshed with the small gear 2-3.

The crankshaft 4 is of an integral structure, a first eccentric wheel 4-4 forming a rotary moving pair with a sliding groove 7-2 at the inner end of the reciprocating rod 7 and a second eccentric wheel 4-5 forming a rotary moving pair with a balancing weight 8 are arranged between the two supporting ends, the diameters of the first eccentric wheel 4-4 and the second eccentric wheel 4-5 are equal, and the circumferential phases are opposite. The outer end of the reciprocating rod 7 is provided with a tool chuck 7-1, and the two ends of the inner sliding chute 7-2 are arc-shaped and are in a runway shape. The relation between the radius R of the end cylindrical section of the crankshaft 4 connected to the upper bearing 4-1 and the eccentricity e of the first eccentric and the radius R of the first eccentric is e + R > R, so that the radial dimensions are as compact as possible. In addition, the distance L between the arcs at two ends of the chute 7-1 at the inner end of the reciprocating rod 7 is larger than (at least equal to) the central distance of the two eccentric wheels and the sum L of the radiuses of the two eccentric wheels, so that the mutual motion balance is facilitated, and the two eccentric wheels 4-4 and 4-5 can be connected with cylindrical sections at two ends of the crankshaft at equal strength.

A sliding insertion piece 7-3 extends from one side of the periphery of the sliding groove 7-2, the other side of the periphery of the sliding groove is fixedly connected with the cylindrical section 7-4, the sliding insertion piece 7-3 is matched with an insertion hole of the rear sliding sleeve 5-2 fixedly connected with the gear box 5 to form a moving pair, and the cylindrical section 7-4 is matched with a through hole of the front sliding sleeve 5-3 fixedly connected with the gear box 5 to form a moving pair.

The assembly protocol was carried out as follows:

firstly, respectively arranging an upper bearing 4-1 and a lower bearing 4-2 into a gear box 5 and a counterweight box 6;

secondly, pressing a large gear 4-3 into a crankshaft 4, and inserting the crankshaft 4 into an upper bearing 4-1;

thirdly, sleeving the front sliding sleeve 5-3 and the rear sliding sleeve 5-2 on the reciprocating rod 7, rotating the crankshaft 4 to a position (shown in figure 2) where the central connecting line of the first eccentric wheel 4-4 and the second eccentric wheel 4-5 is consistent with the length direction of the chute 7-2, and sleeving the reciprocating rod 7 on the first eccentric wheel 4-4 of the crankshaft 4;

fourthly, the front sliding sleeve 5-3 and the rear sliding sleeve 5-2 on the reciprocating rod 7 are arranged in the gear box 5 and fixed;

fifthly, sheathing the balancing weight 8 on a second eccentric wheel 4-5 of the crankshaft 4, closing the balancing weight box 6 to fix the balancing weight box with the gear box 5, and simultaneously inserting one end of the crankshaft 4 into the lower bearing 4-2.

Therefore, after the embodiment is adopted, the two ends of the crankshaft are supported, so that the crankshaft is stable and reliable, and the vibration in use can be more favorably inhibited. In addition, the structural relationship of the sizes of the crankshaft eccentric wheels and the reciprocating rod sliding grooves ensures that the eccentric directions of the two eccentric wheels are consistent with the length direction of the sliding grooves at the inner ends of the reciprocating rods only as shown in figures 2 and 3 during assembly, so that interference can be avoided, the two eccentric wheels pass through the sliding grooves at the inner ends as required, and the mutual penetrating and assembling which is as convenient as a cantilever structure is realized. In addition, the front and rear moving pair structures of the reciprocating rod enable the reciprocating rod to move more stably, and shock absorption is facilitated.

Example two

The reciprocating saw of the present embodiment is shown in fig. 5 to 10, and the basic structure is the same as that of the first embodiment, but the difference is mainly that the crankshaft 4 is not an integral structure, and is formed by combining the crank fulcrum shafts 4.1 and 4.6 at the upper and lower ends and the crank pin shaft in the middle as shown in fig. 9. The crank fulcrum 4.1 or 4.6 is respectively composed of a supporting shaft head and a one-piece crank which symmetrically extends towards two sides from the end part of the supporting shaft head, so that the formed rotary inertia is beneficial to damping, and one side of the crank is provided with an eccentric hole.

The crank throw pin shaft is formed by pressing and mounting an upper pin shaft 4.2 and a lower pin shaft 4.4 which extend reversely through an intermediate spacer 4.3 and two eccentric holes of an intermediate spacer, and the upper pin shaft 4.2 and the lower pin shaft 4.4 are respectively sleeved as a movable fit pin shaft sleeve of a first eccentric shaft 4-4 'and a second eccentric shaft 4-5'. The outer diameter of the two pin shaft sleeves is more than or equal to the width B of the crank throw and the middle spacer.

During assembly, the middle spacer 4.3 is reversely pressed into the pin shafts 4.2 and 4.4 respectively, then sleeved into the pin shaft sleeves 4-4 ', 4-5' respectively, and finally pressed and mounted with the crank throw fulcrum shafts 4.1 and 4.6 respectively; after the press mounting is finished, the supporting shaft heads at the end parts of the crank fulcrum shafts 4.1 and 4.6 are subjected to finish turning or grinding processing so as to ensure the coaxiality of the two supporting shaft heads.

Experiments show that the reciprocating saw of the embodiment has better damping effect in the working process, is very convenient to assemble and has a compact structure. Especially, for the condition of large eccentricity, the width of the inner end chute 7-2 on the reciprocating rod 7 is not influenced by the eccentricity, the size can still be kept small, and meanwhile, the pin shaft sleeves 4-4 ', 4-5' matched with the inner end chute 7-2 are more than the width of the fulcrum shafts 4.1, 4.6 and the middle spacer 4.3 due to the outer diameter, so that the reciprocating rod 7 is easily sleeved on the pin shaft sleeves 4-4 ', 4-5', and simultaneously forms rolling fit, and the performance is better.

In addition to the above embodiments, the present invention may have other embodiments. All technical solutions formed by adopting equivalent substitutions or equivalent transformations fall within the protection scope of the claims of the present invention.

Claims

1. The utility model provides a reciprocating saw, includes that one end is the casing that holds the position, the other end arrangement actuating mechanism, its characterized in that: the output shaft of the motor of the driving mechanism is in transmission connection with a crankshaft, two ends of which are respectively supported in the shell, through a rotary transmission mechanism, a first eccentric wheel forming a rotary moving pair with a chute at the inner end of the reciprocating rod and a second eccentric wheel forming a rotary moving pair with a balancing weight are arranged between two supporting ends of the crankshaft, and the circumferential phases of the first eccentric wheel and the second eccentric wheel are opposite; the reciprocating rod and the balancing weight and the shell respectively form a moving pair moving in opposite directions.

2. The reciprocating saw as defined in claim 1, wherein: the crankshaft is of an integral structure, and the distance between two ends of the inner end sliding groove of the reciprocating rod is larger than or equal to the sum of the center distance between the first eccentric wheel and the second eccentric wheel and the radius of the first eccentric wheel and the radius of the second eccentric wheel.

3. The reciprocating saw as defined in claim 2, wherein: the crankshaft is formed by combining crank throw fulcrum shafts at two ends and a crank throw pin shaft in the middle, the crank throw fulcrum shafts are formed by a support shaft head and a crank throw with an eccentric hole, the crank throw pin shaft is formed by pin shafts extending reversely at two ends of a middle spacer and a middle spacer, and the two pin shafts are respectively sleeved as movable fit pin shaft sleeves of a first eccentric wheel and a second eccentric wheel and are pressed into the corresponding eccentric hole; the outer diameter of the pin shaft sleeve is larger than or equal to the width of the crank throw and the middle spacer.

4. The reciprocating saw as defined in claim 2, wherein: the sum of the radius of the end cylindrical section of the crankshaft and the eccentricity of the first eccentric wheel is larger than the radius of the first eccentric wheel.

5. The reciprocating saw as defined in claim 3, wherein: the diameters of the first eccentric wheel and the second eccentric wheel are equal, two ends of the inner sliding groove of the reciprocating rod are arc-shaped, and the distance between the arcs at the two ends of the inner sliding groove is larger than or equal to the sum of the center distance of the two eccentric wheels and the diameter of the eccentric wheels.

6. The reciprocating saw as defined in claim 3, wherein: the crank throw pin shaft is formed by pressing and mounting oppositely extending pin shafts through two eccentric holes of the middle spacer and the middle spacer, and the two pin shafts are respectively sleeved with a movable fit pin shaft sleeve serving as a first eccentric shaft and a second eccentric shaft.

7. The reciprocating saw as defined in claim 6, wherein: the crank supporting shaft is composed of a supporting shaft head and a connected crank which symmetrically extends towards two sides from the end part of the supporting shaft head.

8. The reciprocating saw as defined in claim 2 or 3, wherein: a gear box is fixedly arranged at the position of the shell, which is close to the output shaft, and an upper end concave embedded with an upper bearing is formed in the gear box; the gear box is fixedly connected with the counterweight box, and the counterweight box is provided with a lower end concave embedded with a lower bearing.

9. The reciprocating saw as defined in claim 8, wherein: the inner spout both ends of reciprocating lever are arc, the peripheral one side of spout extends out the slip sheet, the opposite side links firmly with the cylinder section, the slip sheet forms the sliding pair with the jack adaptation that links firmly in the back sliding sleeve of gear box, the cylinder section constitutes the sliding pair with the perforation adaptation that links firmly in the preceding sliding sleeve of gear box.