JP3076338U - High torsion thrust rod type ratchet spanner - Google Patents

Abstract

(57) [Summary] [PROBLEMS] To provide a pawl spanner with improved torsional force and operability. A push rod (50) has two localization points (54) in a slideway (36). The pawl 52 is elastically meshed with the ratchet 40 at the localization point 54. The cross section of the slideway 36 has a direction of a first diameter C parallel to the plane of the pinching end 32 and a direction of a second diameter D perpendicular to the direction of the first diameter. It is longer than the length of the direction. The cross section of the slideway 36 and the push rod 50 is formed in an elliptical or rectangular shape. Changing the engagement position of the thrust bar and the ratchet wheel further increases its acceptable torsional force, as well as increasing the sensitivity of the ratchet wheel action. In addition, the minor axis direction D of the slideway 36
It does not increase the length of the wrench, nor does it increase the thickness of the spanner, so that it can be used where space is tight.

Description

[Detailed description of the invention]

[0001]

[Technical field to which the invention belongs]

 The present invention relates to a push-rod type ratchet wrench.

[0002]

[Prior art]

 A conventional push-rod ratchet wrench, as shown at 10 in FIG. The handle body 11 and the ratchet wheel 14 are placed in through holes in the head 12 of the handle body 11 and are rotatable. The pushing rod 16 is a rod having a circular cross section, and has pawls 17 on two sides thereof. The push rod 16 slides on a slideway 13 provided through the head 12 and can be positioned at two positions by being stopped by the elastic unit 18. The left and right pawls 17 mesh with the ratchet wheel 14 to form the function of a one-way ratchet in different directions.

[0003]

[Problems to be solved by the invention]

 However, such a configuration cannot accept a high torsional force, and has the following disadvantages on the operating surface. When the handle body 11 of the spanner is pushed counterclockwise in the state of FIG. 1, a latching action is formed between the ratchet wheel 14 and the pawl portion 17 of the pushing rod, so that the handle rotates in the same direction as the ratchet wheel. It becomes possible. At this time, an operating force F from the pawl portion 17 along the cutting line direction of the ratchet wheel acts on the tooth portion of the ratchet wheel 14. The vertical component Fy of the acting force F points to the pawl. And its action position is near the center of the pawl. Since the ratchet has a hollow structure, its strength is relatively low. When the acting force F reaches a considerable strength, if the vertical component force Fy becomes larger than the bending resistance of the ratchet, The pawl is deformed and damaged, and cannot be used.

As shown in FIG. 2, in the operation process of FIG. 1, the ratchet wheel 14 also applies one reaction force F ′ to the pushing rod 16. Since the pushing rod 16 has a single-core structure, it can receive the vertical component force Fy ′, but if the lateral component Fx ′ is too large, the pushing rod can be hung on the slideway 13. It cannot be used.

Next, when the wrench is moved in the clockwise direction, as shown in FIG. 3, the push rod 16 is pushed rightward by the ratchet wheel 14 to be separated from the ratchet wheel 14 and moved away from the ratchet wheel 14. Form action. Since the contact position A and the included angle θ in the direction of the handle body axis are relatively small, when the pawl 141 of the ratchet wheel pushes the pawl 17 on the slope S, as shown in FIG. The vertical component n2 of the acting force N acts on the thrust bar and presses the thrust bar 16 against the inner wall of the slideway 13, causing the thrust bar 16 to have a relatively large coefficient of friction. For this reason, the ratchet cannot move the pushing rod sideways without a relatively large acting force, so that the operation of the ratchet cannot be ensured. The ratchet 191 and pawl unit 192 of the other types of ratchet spanners 19 shown in FIGS. 5 and 6 have similar disadvantages. Therefore, the main purpose of the present invention is to increase the torsional force and operability of the ratchet wrench.

[0006]

[Means for Solving the Problems]

 To achieve the above object, the ratchet wrench according to the present invention has two localization points in the slideway. The pawl is elastically engaged with the ratchet at the stereotactic point. The cross section of the slideway has a first radial direction parallel to the pinch end surface and a second radial direction perpendicular to the first radial direction. The length in the first radial direction is greater than the length in the second radial direction. Is also long.

In the ratchet wheel wrench according to the second aspect of the present invention, the cross sections of the slideway and the push rod are formed in an elliptical shape. The ratchet wrench according to the third aspect of the present invention has a slideway and a cross section of a push rod formed in a rectangular shape. According to the fourth aspect of the present invention, the ratchet wrench according to the fourth aspect of the present invention is configured such that the engagement range between the ratchet and the pawl portion of the pushing rod and the included angle for the shaft of the handle main body are between 30 degrees and 55 degrees. .

SUMMARY OF THE INVENTION The present invention has been made to solve the above-described object, and has a ratchet-type ratchet wheel wrench in which the engagement positions of the pawls and the ratchet bar pawls are changed. Achieve the purpose of increasing torsional force and operability.

[0009]

[Embodiment of the invention]

 Hereinafter, embodiments of the present invention will be described with reference to the drawings. As shown in FIGS. 7, 8, and 9, the push-rod ratchet wrench 20 provided by the embodiment of the present invention includes the following. One end of the handle main body 30 is provided with a stopper end 32 and a through hole 34. The slideway 36 is provided to penetrate the stopper end 32 laterally and communicates with the through hole 34 at the same time.

The cross section of the slideway 36 is elliptical, and has a radial direction C parallel to the plane of the pinching end 32, a radial direction C, and a radial direction D perpendicular to each other. The length in the radial direction C is longer than the length in the radial direction D. The ratchet 40 has a hollow fitting hole 42 into which a nut or bolt is fitted. A large number of continuous tooth portions 44 are provided on the outer periphery. The ratchet 40 is rotatable in the through hole 34 and is restrained by the groove 35 and the C-shaped ring 39 in the through hole.

The pushing rod 50 is a rod body having an elliptical cross section, and has a horizontal radial direction G and a vertical radial direction H. The length of the radial direction G is longer than the radial direction H. The leading edge of the push rod has a slightly concave arc shape, and two pawls 52 are provided on two sides thereof. The push rod 50 is placed in the slideway 36 and is capable of sliding movement. As shown in FIG. 10, G in the radial direction and H in the radial direction are separately added to the radial directions C and D of the slideway.

The localization unit 60 includes a spring 62 and a ball 64. The orientation unit 60 is located in the recess 37 of the handle body 30 and resiliently locates into one of two orientation portions 54 at the trailing edge of the push rod 50. As a result, the push rod 50 has two localization points in the slideway. Each localization point can resiliently engage one pawl 52 with the ratchet tooth 44.

[0013] The operation of the ratchet when driving the fitted screw part of the present invention is the same as the conventional one. In the state shown in FIG. 11, the push rod 50 is located at one localization point, and the right pawl 52 is engaged with the ratchet wheel 40. The range of engagement between the two is between 34 degrees and 47 degrees. When the handle body 30 is pushed in the reverse direction of the clock, the pushing rod drives the ratchet wheel to rotate in the same direction to drive the screw-fitted parts. Since the length of the push bar in the horizontal radial direction G is longer than the length of the conventional push bar, the pawl portion 52 is relatively high, so that the ratchet wheel is engaged at a relatively high position. The axis directions of P and the handle body 30 form one relatively large angle of inclusion δ. In the contact position, the pawl 52 acts on the tooth 44 of the ratchet 40 with an acting force F. The vertical component force Fy of the acting force F points toward the pawl. However, since the contact position P has already changed, the position where the vertical component force Fy has acted further approaches the real center portion Q on the outer periphery of the ratchet wheel. To do this, they move farther away from the center of the pawl. As a result, the ratchet wheel 40 is strong and can receive a higher torsional force.

Next, as shown in FIG. 12, in the operation state of FIG. 11, the ratchet 40 applies one reaction force F ′ to the pushing rod 50. However, since the meshing position is higher than the conventional one, the lateral component Fx 'of the reaction force F' decreases. This reduces the chance that the push rod will be trapped on the slideway.

As shown in FIG. 13, when the wrench is operated in the clockwise direction, the ratchet wheel 40 pushes the pawl 52 to the right, thereby separating the pushing rod 50 from the ratchet wheel, Form the action of the ratchet. When the inclined surface r of the tooth portion 44 of the ratchet wheel 40 urges the pawl portion 52, the acting force N 'is slightly a horizontal component force n. Therefore, the applied force of the ratchet wheel is somewhat reduced. Moves the thrust bar 50 sideways, and the vertical component that pushes the thrust bar against the inner wall of the slideway 36 is small, whereby the coefficient of friction of the thrust bar is greatly reduced, and the ratchet wheel 40 can easily push the thrust bar 50. It moves and slides to increase the sensitivity of the action of the car.

FIG. 14 shows another embodiment of the present invention, in which the cross section of the slideway 74 in the stop end 72 of the spanner 70 is slightly rectangular, and the cross section of the push rod 75 is also rectangular. The major axis direction I of the slideway 74 and the push rod 75 is similarly parallel to the plane of the pinching end 72, and the minor axis direction J is perpendicular to the plane of the pinching end 72.

[0017]

[Effect of the invention]

 The present invention changes the position of the engagement between the push rod and the ratchet to further increase its acceptable torsional force and increase the sensitivity of the ratchet action. Further, as shown in FIG. 10, the spanner of the present invention does not increase the length of the slideway 36 in the short diameter direction D and does not increase the thickness of the spanner, so that it can be used where space is narrow. It is. The relationship between the cross-sectional ratios of the pin stop 32 is related to the strength of the entire spanner.

The cross-sectional area of the retaining end: U = width H × thickness W The remaining cross-sectional area of the retaining end: V = width H × (W−2T), and according to the experimental values of the present inventors, The safety coefficient S is as follows. S = V / U = (W-2T) /W=0.24 to 0.37

[Brief description of the drawings]

FIG. 1 is a partial cross-sectional view of a conventional push-rod type ratchet wheel spanner.

FIG. 2 is a state diagram of a reaction force in FIG.

FIG. 3 is a diagram showing a state in which a wrench is rotated and moved in the same opposite direction as that of FIG. 1;

FIG. 4 is a partially enlarged view of FIG. 2;

FIG. 5 is a sectional view of another type of conventional ratchet wheel.

FIG. 6 is a cross-sectional view of another conventional ratchet.

FIG. 7 is a perspective view showing a ratchet according to an embodiment of the present invention;

FIG. 8 is a three-dimensional view showing the disassembled state body of FIG. 7;

FIG. 9 is an enlarged three-dimensional view showing a pushing rod of FIG. 7;

FIG. 10 is a side view of FIG. 7;

11 is a cross-sectional view showing a state where the front local portion and the spanner of FIG. 7 are turned and moved.

FIG. 12 is a view showing a state of a reaction force of FIG. 11;

FIG. 13 is an enlarged view of a local area similar to FIG. 6, showing a state where a spanner is turned and moved in the opposite direction.

FIG. 14 is a side view of another embodiment of the present invention.

[Explanation of symbols]

 Reference Signs List 20 ratchet wheel spanner 30 handle 32 pinching stop end 34 through hole 35 groove 36 slideway 37 concave portion 39 C-shaped ring 40 ratchet wheel 42 fitting hole 44 teeth 50 pushing rod 52 pawl 54 positioning position 60 positioning unit 62 spring 64 Ball 70 Ratchet wheel spanner 72 Entrapment stop end 74 Slideway 75 Push rod

Claims (4)

[Utility model registration claims] An end of a handle has a stopper end provided with a through hole, and the stopper end has a slideway penetrating laterally and communicating with the through hole. A pawl wheel provided with a handle main body having a plurality of continuous teeth on the outer peripheral surface is rotatably provided in the through hole, and a pawl portion is formed on two sides of the front edge. A pushing rod is provided slidably in the slideway, and the localization unit is located on the pushing rod by elasticity,
The push rod is provided in the handle body, the push bar has two localization points in the slideway, and one pawl is elastically meshed with the ratchet wheel at each one of the localization points, The cross section of the road has a first radial direction parallel to the pinching end plane and a second radial direction perpendicular to the first radial direction, and the length in the first radial direction is the second radial direction. High-torsion thrust bar-type ratchet wrench characterized by being longer than its radial length. 2. The high-torsion thrust bar ratchet wrench according to claim 1, wherein the slideway and the thrust bar have a cross section formed in an elliptical shape. 3. A high-torsion thrust bar ratchet spanner according to claim 1, wherein the slideway and the thrust bar have a rectangular cross section. 4. The method according to claim 1, wherein a meshing range between the ratchet and the pawl portion of the push rod and an included angle of the handle main body with respect to the axis are 30 degrees or more and 55 degrees or less. High torsion thrust rod type nail wrench.