JPS6025701A - Chain saw with prime mover - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a motorized chainsaw having a guide rail that directly guides a saw chain driven by a motor, the guide rail having a front end portion that extends forwardly. It is of the type having an approximately semicircular forward deflection section for deflecting the chain L80 from the feed side where it is moved to the return side where it is moved rearward.

J! i
! It is known that it is mainly determined by 41+shi. Chain tension is also one of the factors that determines the service life of the guide rail, since as the chain tension increases, the load that causes wear on the guide rail also increases. The saw chain is located at the rear end of the guide rail within the scope of the prime mover, that is, the prime mover [1! Driven by a chain drive gear at the end of l. In this case, the feed side of the U-saw chain is moved forward. The saw chain runs 180' along the approximately semicircular deflection section at the front end of the guide rail.
As it is deflected, the return side is forced to move rearwardly towards the chain drive gear. The return side is under a tensile load, while the feed side is under pressure and slack. Frictional loads occur in the area of the front deflection section, which directly guides the saw chain. At the entrance of the chain deflection section, i.e. at the 12 o'clock deflection point, the chain tension or frictional load is extremely small, but at approximately 135 degrees, at approximately 4 o'clock and 5 o'clock positions, the largest frictional or wear load occurs. brought about. Therefore, the service life of the guide rail is determined by the durability of the area that receives the greatest frictional load. In practice, this range is usually reinforced by additionally fitting hard metals.

Friction and wear can be reduced by reducing the load rate per unit length of the guide rail.

In other words, reducing wear is achieved by deflecting the saw chain along as large a guide curve as possible.

Problems to be Solved by the Invention It is an object of the present invention to provide a guide rail in which the saw chain can be deflected with less wear in the front region of the guide rail, and which has a deflection section suitable for manufacturing the deflection curved section. The object of the present invention is to improve the motorized chainsaw mentioned in the introduction in such a way that a satisfactory rail head construction is obtained in the rail.

Means for Solving the Problems The means of the present invention for solving the above-mentioned problems is that in a motorized chainsaw, l" (iill is 9
The guide r of the curved portion extending over 0° includes a portion of the curved tip arc section that is within the range of the longitudinal central axis of the guide rail, and a curved tip arc section that transitions into the longitudinal guide of the guide rail. The curved line section is arranged between the circular arc section and the curved end circular arc section and at least substantially follows the drawn line.

Advantageous embodiments of the invention are disclosed in claims 2 to 16-1.

The guide rail 1.1' shown in the first embodiment belongs to a motorized chainsaw, and the guide rail 1.1' according to the invention
is secured to the motor chain saw by its rear end section. In order to be able to use the upper and lower guide rails alternately as is well known, the guide rails 1°l are constructed symmetrically with respect to the longitudinal central axis 2.2'. .Soj 1゛Rail 1. l', l
The endless saw chain ``rffi3ff'' is moved forward in the direction of the arrow 42 with the feed side supported on the upper longitudinal guide 3.3', and is turned 180° at the forward turning point 4-. , then the lower longitudinal guides 5, 5'
With the return side guided by , it is moved rearward in the direction of the arrow towards a chain drive gear driven by a prime mover, not shown in detail.

In order to obtain a saw chain guide with less wear in the area of the deflection section 4' shown in FIGS. 2 and 3, the upper transition section 7.7' and the lower (IIll transition section δ, 8 ' Guide curved portions 6, 6' extending over approximately 160° between
A curved tip arc section 9, formed between two contact points T, T2 in the front region where are on the longitudinal central axis 2, 2'.
9' and guide rails 1,1 are constructed. Therefore, one part of the curved tip arc section 9,9' extends downwardly from the longitudinal central axis 2.2' to the lower contact point T2. It extends to T'2, while the curved tip is wide 1
5 L angle 1 center axis 2 in the capacity part of arc section 9, 9'
, 2 upwardly to the contact point T2°·]·′ on the − side.

In the first embodiment shown in FIG. 2, f'5 is followed by f15 arc section 9, rJ, both line sections which follow at least approximately or exactly the course of the drawn line], 0. The double line section 10 extends over 900 mm and is formed between the lower contact T2 and the 1.- side contact T in the area of the part 1.1 of the guide 1 on the . In this embodiment, which is mirror-symmetrically configured with respect to the vertical central axis m2, the upper guide 12 portion 12 extending over 90° of the guide curved portion 6 has a drawing line calculation formula, or has a calculation formula for both lines. There is a /lis'1 line segment 10 identical to the above vortex line segment, constructed so as to at least approximate the equation. Therefore, the double line section 10 of the center line 10 is formed between the upper contact point T1 and the contact point T-1 located above it.

I? A four-curved end arc section 13 follows. The curved end arc section 13 is formed between the lower contact point T and the lower transition section 8 . Both line sections 10 are therefore located between the curved end arc section 13 and the curved tip arc section 9. Guide curved part 6
Similarly, the upper guide part 12 has a curved end arc section 13.
is arranged, and the curved end arc section 13 is connected to both upper line sections, and the upper contact point T1 and the side transition section 7
is located between.

A lower longitudinal guide 5 continues from the transition section 8 in the lower curved end arc section 13 . Similarly, the upper curved end arc section 13 is followed by a longitudinal guide 3 on the negative side of the guide rail 1 from the transition section 7 . two longitudinal guides 3, 5
does not extend linearly parallel to the longitudinal central axis 2, but is of curved construction, so that the two longitudinal guides δ, 5 have a convex-shaped course relative to the longitudinal central axis 2. It can be seen from Fig. 2 that the

The guide rail 1 shown in FIG.
The upwardly extending part and the downwardly extending part, the two line sections 10 on the two sides and the two line sections 10 on I' 11.111, the upper curved end arc section 13 and the lower curved end arc section 1.
3 and l 1. The ill longitudinal guide r3 and the lower vertical guide [5 have exactly the same shape as JT, respectively. By configuring the guide rail 1', which has a guide rail 1' having a curved section 6 as a deflection section, in a mirror-symmetrical manner, the guide rail 1' is made up of different curved sections that are arranged in a series, so that the guide rail 1' can be moved around the longitudinal central axis 2 as needed. Since the guide rail 1 can be reversed by 180° to change the lower part of the guide rail 1, it is possible to use the guide rail 1 without the middle L portion.

The radius H of the curved end arc section 9 is advantageously selected to be significantly smaller than the radius R1 of the curved end inner arc section 13. In this embodiment, the radius R of the curved end arc section 13,
The radius R6 of the curved tip arc section 9 is about twice to ten times as large. The optimum dimensional relationship between the arc sections is provided in this example, with radius R4 of curved end arc section 13 being about seven times the radius R3 of curved tip arc section 9.

The guide section of the curved tip arc section 9 in front of the turning section cow is set to be relatively small RI with respect to the line section of the guide curved section 6, and has a radius of about 3 ~], 0 of the line section of the guide curved section 6. % is advantageous. A particularly advantageous configuration is obtained if the distance of the guide section of the n-bent arc section 9 is approximately 5% of the line section of the guide bend 6 between the two transitions 7.8.

From the viewpoint of manufacturing the guide rail 1 economically using a machine, in this embodiment, the two drawn line segments 10 between the curved tip arc segment 9 and each curved end arc segment 13 are It is configured to be assimilated into arc sections. The radius R8 of both line segments 100 is larger than the radius tag of the curved end arc segment 9 of the curved end arc segment 1.
3 is advantageously smaller than the radius R1. Drawing line classification 10
The radius R8 is approximately 12 to 12 times the radius R6 of the curved tip arc section 9.
It may be twice as much. In particular, it is advantageous, as in the case of this embodiment, to configure the radius RS of the drawn line section 10 to be approximately 1.6 times the radius R5 of the curved tip arc section 9.

After this, the l curve 'Ali part arc section 13 I'('
f = I1 is approximately 25 to 1' of the drawing line section 10/diameter Rs
It is selected so that 5 times 11 (=. In this case, as in the guide F rule 1 of 1 series of tree nuts, the 1' A particularly advantageous configuration with respect to chain deflection with low wear is obtained if the chain is chosen so that

Furthermore, it is advantageous for the guide rail 1 to be constructed in such a way that the radius R of the convex tip arc section 9 is smaller than the width of the guide rail between the lower transition section 7 and the lower transition section 8. . In the guide rail 1 according to the present invention, the radius R8 of the drawn line section 10 is approximately equal to the guide rail width between the upper transition section 7 and the lower transition section 8 at both ends of the guide curved section 6. Or, it is particularly advantageous to make the width not larger than -2.It is advantageous to approximate the drawn line segment 10 to a circular arc section in production.To calculate the sum /c9, 1, the contour line of the drawn line section 10 transitions tangentially into arc sections (curved tip arc section 9 and curved end arc section 13) at the apex of the guide rail 1 and at the body of the guide rail, respectively. The parameters of the drawn curve are determined by the tangent condition, the guide rail width, the position of the contact point, and the correction coefficient Kφ determined by experiment. In order to give the rail a reversible shape, the contour of the line section 10 is designed symmetrically with respect to the longitudinal central axis 2.

In the design and dl calculation of the guide rail 1 according to the present invention,
B is the guide rail width, R1 is the radius of the curved end arc section 13, R3 ((p) is the radius of the drawn line, R3 is the radius of the curved tip arc section 9, Ml is the center of the curved end arc section 13, M
3 is the center of the curved tip arc segment Q, M8 is the origin of the drawn line, μ is the damping coefficient, Kφ is the correction coefficient determined by experiment, and R8φ is the starting radius of the drawn line.

In a guide rail l that is optimally designed both in terms of economical production and in terms of the occurrence of a very low friction of 1°, the radius R3 of the curved tip arc section 90 is 30 mIn. The radius of the drawn line segment 10 that approximates a circle is Rs 48 mm.
and l'il R411 of the curved end arc section 13
, L, and B are significantly larger at 200 mm.

Second Embodiment The second embodiment shown in FIG. 3 is basically constructed in the same manner as the first embodiment. However, in FIG. 3, parts corresponding to those in FIG. 2 are indicated by adding a dash to the reference numeral of the part. In order to make it easier for the person J11 raw P1'; in this embodiment, the upper and upper drawn line segments 10, which at least approximately follow the drawn lines, are divided into at least two segments, each having a radius R' and a radius. ff1J has been completed.゛I-diameter 1 (' is indicated by the segments T1 and T3 with radial radius and by the segments T, ′ and T;
and T6′.

T2' is defined in such a way that the entire line section from T2 to T211, designated lO, follows at least approximately one line. The two radii R'R are larger and smaller than the radius R of the curved end arc section 13'.

Furthermore, the radii R and R' are each about 1.2 to 2 times, preferably about 1.6 times, the radius R'3 of the curved arc segment 9'.
It's double. In this embodiment, the radius R1 of the curved end arc section 13' is equal to the radius R3 of the curved end arc section 9 of the turning section.
This is approximately 25 times the number. Furthermore, radius I (1 is the direction change part hand)
The radius R' of the drawn line segment 10 that approximates the arc of is still R
'8 approximately 12 to 1-7 times, preferably 13°5 to 16.6
It's double. The other structural configurations of this embodiment correspond to those of the first embodiment.

Effects of the Invention With the guide rail constructed as in the present invention, the load factor can be significantly reduced, and as a result, the initial friction force and the amount of wear can be reduced.

The reduction in the amount of wear resulted in a clear extension of the service life.

The thermal load on the deflection section of the rail head is more uniform and lower than in known guide rails. This results in less stretching of the chain due to thermal loads, a more constant chain tension and a quieter sawing process. Furthermore, as a result of the less heat generated, improved lubrication properties at the deflection section are obtained. The non-circular deflection section with a series of curved sections makes full use of the guide rail/is constructed symmetrically in ζ, ie as a solid rail with interchangeable upper and lower sides. Because the friction (Ll loss) is smaller than that of conventional guide rails, a higher cutting efficiency is achieved.The larger radius at the deflection section makes the parting characteristics more remarkable than that of conventional guide rails. In addition to this, the vibrations that occur during this nine-glue operation are also significantly reduced.

[Brief explanation of drawings]

1 is a side view of a motorized chainsaw having a guide rail and a saw chain; FIG. 2 is a partial view of an embodiment of the guide rail according to the invention; and FIG. FIG. 3 is a partial diagram of an IN example.

Claims (1)

[Scope of Claims] 1. A prime mover chainsaw having a guide rail for directly guiding a saw chain driven by the prime mover, the guide rail having a front end portion that is configured to move forward (from l to rearward). Return ■! In the type that has an approximately semi-circular front deflection section for changing the direction of the rehe chain by 180 degrees, the deflection section (
4. The curved part of the guide rail (11;
A part of the curved tip arc section (9; 9) within the range of the longitudinal central axis (2; 2') of the guide rail (; 1');
The curved end arc segment (13:13), the curved tip arc segment (9; Q'), and the curved end arc segment (13; 13)
) and a drawn line section (10; 10') which at least approximately follows the drawn line. 2 The guide rail (1; 1) is aligned with the vertical center axis (2; 2')
), and the forward deflection part (4
The curved tip arc section (9; 9) provided in the range of the vertical center of 1111 line (2:2') of The guide rail (1; 1) is in instant contact with two consecutive drawn line sections (10; 10) and each drawn line section (10; 10), respectively.
')' consists of two curved end arc sections (1δ; 13') transitioning into two side longitudinal guides (3; 3') and a lower longitudinal guide (5; 5'). Motorized chainsaw according to claim 1, characterized in that it has a substantially semicircular guide bend (6; 6'). . 3. Drawing line division (10°10') of direction changing part (4; 4')
), the curved tip arc section (9:9') within the vertical center axis (2.2') range is the radius (R,;R) of the curved end arc section (13, 13'). . 4. The radius (R1) of the curved end arc section (13) is approximately 4 of the radius (R3) of the curved end arc section (9) of the direction change part (cow).
~10 times the special ML ('motorized chainsaw according to claim 3) 〇5, radius (R1') of the arc section (13') of the curved Mta part
is the radius (
A motorized chain according to claim 3, wherein R1) is approximately 25 times larger than R1). 6. The drawn line segment (10) between the curved tip arc segment (9) and the curved end arc segment (13) of the deflection portion (4) is larger than the radius (R3) of the curved tip arc segment [9]. Any one of claims 1 to 2, which is large and approximates an arc segment having a radius (R) smaller than the radius [R1] of the curved end arc segment (1, 3). Motorized chainsaws as described in Section 1. 7. The drawn line segment (10) is the radius (R> and (R, W)
It is composed of at least two divisions with
and (ft'4) is larger than the radius of the curved end arc section [9'] and smaller than the radius (R1) of the curved end arc section (13'), Special 1st work'
1. A motorized chainsaw according to any one of claims 1 to 3. 8, θ drawn line segment (10; 10
) is approximately 1.2 to 2 times the radius (R; R') of the curved tip arc section [9°9] of the inside of the variation [4; cow']. , Particular i': The motorized chainsaw according to claim 6 or 7. 9. The radius (R1) of the curved end arc section (13) is similar to the arc section of the direction changing section (4). The motorized chainsaw according to any one of claims 1 to 8, which is approximately 2.5 to 5 times the radius (R8) of the drawn line section (10). The radius [R'] of the end arc section (13') is about 12 to 17 times the radius (R' and R'S) of the drawn line section (10') that approximates the arc section of the direction change part (4). be,
fIfg'+' A motorized chainsaw according to any one of claims 1 to 8. 11. Arc section (9,
9) radius (R3:R1) of the two longitudinal guides (3,
5; 3', 5) is smaller than 7 of the guide rail width between claims 1 to 10.
In the motorized chainsaw 12 according to item 1, the radius (R8; R', R'8) of the drawn line segment (1o; 1o') that approximates the arc segment is two curved end arc segments (13) facing each other. ; T3 ) is equal to or slightly larger than 7 of the guide rail width between the two contact points (T1; T', ); The motorized chainsaw described in item 1. 13. Curved tip arc section (9; 9) of direction change part (cow: 4)
') Guy P section is curved end arc section (13; 13')
is about 3-10% of the total guide section between the transition parts (7, 8; 7'. 8), ! 1q
A motorized chainsaw according to any one of claims 1 to 12. 14, the guide rail (1; 1) following the two curved end arc sections (13;
), the two longitudinal guides r (3, , 13, 5') are curved convexly with respect to a vertical center line, 4'
#3'r A motorized chainsaw according to any one of claims 1 to 13. 15. Motorized chainsaw according to any one of claims 1 to 14, in which the line drawing section (10; 10') strictly follows the course of the line drawing. 16. The drawn line segment (10; 10) is formed according to the formula: B is the guide rail width, R is the radius of the drawn line, S(ψ) μ is the friction coefficient, and Rsφ is the starting radius of the drawn line. Range 1st to 15th
A chainsaw that uses the prime mover described in any one of the following paragraphs.