KR940005242Y1 - Apparatus for extracting juice - Google Patents

Abstract

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Description

Green juice maker

1 is a cross-sectional view showing the configuration of a conventional green juice maker.

Figure 2 is a cross-sectional view showing the configuration of the green juice maker according to the present invention.

Figure 3 is a partially enlarged cross-sectional view showing a first embodiment of the elastic pressing means used in the present invention.

Figure 4 is a partially enlarged cross-sectional view showing a second embodiment of the present invention elastic crimping means.

Figure 5 is an exploded perspective view showing the configuration of the mechanism of the third embodiment of the present invention elastic crimping means.

6 (a) and 6 (b) are partial enlarged cross-sectional views incorporating the third embodiment of FIG. 5, respectively, with FIG. 6 (a) being a release state and FIG. 6 (b) being a cross-sectional view of a compressed state. admit.

* Explanation of symbols for main parts of the drawings

G1, G2: crush gear G1: main gear

G2: driven side gear S11 ~ S22: rotating shaft

B, B ': Bushing

10, 20, 30: elastic bias means

11: boss section 12: spring

13: adjusting screw 15: cap

21: cam 23: release surface

24: pressing surface 31: end cam (end cam)

32: Main Cam 33: Follow Cam

The present invention relates to a green juice maker.

The green juice making machine which manufactures green juice from vegetables or fruits is conventionally mainly used as a mixer or centrifugal separation method. However, the juice is pulverized by crushing the material between two crush gears. A green juice maker appeared as shown in FIG.

In FIG. 1, a housing (houshig H) containing two grinding gears (G1, G2) and a juice net (not shown for convenience) is coupled to a main body M including a drive unit such as a drive motor. Each grinding gear (G1, G2) is formed in the form of a helical gear (helical gear) is provided with a crushing portion (K) which is toothed to each other, and the transfer portion (T) in the form of Archimedes screw (Achimedes screw) extending therefrom, Rotating shafts S11, S12, S21 and S22 extend at both ends thereof.

Since both grinding gears G1 and G2 are toothed with each other, both grinding gears G1 and G2 may be driven simultaneously by driving only one grinding gear G1. Accordingly, the grinding gear G1 shown in the upper side of the drawing becomes a driving side gear, and one end of the driving shaft extends from the driving part of the main body M to the neck N through the through hole P11. The rotary shaft S21 of the remaining driven side gear (grinding gear G2) is rotated and supported by the shaft support groove P21 formed at the end of the main body M. Meanwhile, the other side rotation shafts S12 and S22 of the two grinding gears G1 and G3 are rotatably supported by the shaft support grooves P12 and P22 formed inside the housing H, respectively.

In such a configuration, in order to smoothly rotate the grinding gears G1 and G2, bushings B and B 'of appropriate materials are provided in the through holes P11 and the shaft support grooves P12, P21, and P22. It is preferable.

The material of such bushings (B, B ') is suitable for elastic bearing materials such as butyl rubber. If such bushings (B, B') are used, two grinding gears (G1, G2) may be used. Clearance of the liver is increased, there is a problem that the grinding force is lowered. That is, in order to sufficiently pulverize the fibers of the material, it is desirable to minimize the gap to be close to zero by appropriately adjusting the teeth, the pressure angle and the center distance of the grinding portion K of the two grinding gears G1 and G2. Do. However, in the case of using the bushings B and B 'of the elastic bearing material, the bushings B and B' are deformed by the load of the material injected between the two grinding gears G1 and G2, and the gap therebetween increases. This causes a problem that the grinding efficiency is lowered.

On the other hand, even if the bushings (B, B ') are not used, the processing and assembling of the green juice making machine with zero clearance between the two grinding gears (G1, G2) is impossible, and in this case, when the grinding gears (G1, G2) are rotated, Noise and abrasion of the rotating shaft (S11 ~ S22) had a serious problem.

In addition, the gap between the grinding gears (G1, G2) is increased due to wear and tear due to repeated use of the green juice maker, and there was no conventional method of controlling this at all, even if the appropriate grinding force varies depending on the type of material to be added. Therefore, the conventional green juice maker can only extract the green juice from the material, it is impossible to extract the fiber beneficial to the human body.

In view of such a conventional problem, the object of the present invention is that even if the green juice maker is manufactured with a relatively large tolerance, the gap between the grinding gears can be minimized to achieve perfect tooth coupling, and the green juice maker can be ground according to the wear or material of the green juice maker. It is to provide a juice maker that can control the force.

In order to achieve the above object, the green juice production machine according to the present invention is a green juice production machine comprising a pair of grinding gears, each of which is supported by rotating shafts of both ends between a main body including a drive unit and a housing coupled to the main body, a pair of mills And an elastic crimping means for elastically pushing the rotary shaft of any one of the crushed gears toward the other crushed gear.

Specific features and other advantages of the present invention will become more apparent from the following description of the preferred embodiments with reference to the attached drawings.

In FIG. 2, two grinding gears G1 and G2 on which one rotation shaft S12 and S22 are axially supported by bushings B inserted into the shaft support grooves P12 and P22 at one end of the housing H are respectively rotated to the other rotation shaft. S11 and S21 are coupled to the main body M side including the drive section.

The two grinding gears G1 and G2 have a grinding part K formed in the form of a helical gear and a transfer part T formed in the form of an Archimedes screw, as shown in the related art, and are geared to each other in the grinding part K. Accordingly, one of the two grinding gears G1 and G2 is coupled to the drive shaft S whose rotary shaft S11 extends from the drive portion of the main body M through the through hole P11, and the other one extends from the main body M. Is rotated and supported by the shaft support groove (P21) of the neck (N). Accordingly, the two grinding gears G1 and G2 may be divided into a main gear G1 and a driven gear G2. Hereinafter, the two grinding gears G1 and G2 may be classified as necessary and the two may be referred to as grinding gears G1 and G2. Let's do it.

The other side rotation shafts S12 and S22 of the main gear G1 and the driven gear G2 are rotatably supported by the shaft support grooves P12 and P22 formed in the housing H, respectively. Preferably, each of the rotating shafts S11 to S12 of the grinding gears G1 and G2 is supported by bushings B and B 'made of a suitable bearing material, which bushing B is formed in a rough cup shape. And the bushing B 'supporting the rotary shaft S11 coupled to the drive shaft S in the main gear G1, is accommodated in the shaft support grooves P12, P21, and P22. Is formed.

According to the characteristics of the present invention, the rotary shafts S11 to S22 of the grinding gears G1 and G2 are provided with elastic crimping means 10 in a direction orthogonal thereto, so that the two grinding gears G1 and G2 are closely contacted with each other so that there is no gap. do. In FIG. 2, the boss part 11 is extended to the neck N of the left side of the figure, and one side of the housing H of the right side of the figure, respectively, and the inner diameter part of this boss part 11 is shown. The spring 12 and the adjustment screw 13 are accommodated. A screw portion is formed in the inner diameter portion of the boss 11 so that the pressing force of the spring 12 changes as the knob 14 of the adjusting screw 13 is turned.

Preferably, the boss portion 11 is provided in the direction of rotation shafts S21 and S22 of the driven gear G2. When the adjustment screw 13 is introduced into the boss portion 11, the rotation shaft of the driven shaft gear G2 is provided. The elastic pressing force on the bushing B of (S21, S22) is increased so that the driven side gear (G2) comes into close contact with the main side gear (G1), so that the gap between them is close to zero, resulting in a complete close contact with the material. The force is increased. On the other hand, if the adjusting screw 13 is retracted with respect to the boss 11, the elastic pressing force between the driven gear G2 and the main gear G1 is lowered and the grinding force is reduced.

Therefore, the present invention elastic compression means 10 can adjust the grinding force by adjusting the gap between the two grinding gear (G1, G2) as necessary.

3 shows a particularly preferred embodiment in the case of implementing such an elastic crimping means, in which the caps 15 are provided on both sides of the spring 13 to adjust the adjusting screw 13 and the bushing B, respectively. Proper transmission of the elastic compressive force between the two ends is achieved.

Meanwhile, FIG. 4 shows another embodiment of the inventive elastic crimping means 20. In this embodiment, a screw is formed in the boss portion 11 to screw the adjustment screw (13 in FIGS. 2 and 3). Instead, a cam 21 rotating around the hinge 22 is employed. The cam 21 is provided with a predetermined release surface 23 and a pressing surface 24 whose radial distance from the hinge 22 is larger than this release surface 23, and a user-operated handle 25 is provided. It is extended. Hinge 22 is coupled to the main body (M) or the housing (H), so that the cam 21 can be rotated to the pressing position and the release position around it. The state shown by the solid line in the figure is a crimping position where the crimping surface 24 of the cam 21 comes into contact with the cap 15 to closely contact the two grinding gears (only the driven gear G2 is shown in the drawing), and the dotted line The state shown by is the release position for releasing this close contact.

On the other hand below 5 is shown another embodiment of the present invention the elastic pressing means 30, in which the elastic pressing means 30 is provided with an end cam (end cam; 31).

The end cam 31 is composed of a main cam 32 and a driven cam 33, both cams (32, 33) having inclined surfaces (34, 35) in contact with each other and the plane (36, 37) on the opposite side In this case, the handle 36 extends on the plane 36 of the main cam 32 and the plane 37 of the driven cam 33 is in contact with a spring or its cap (not shown in FIG. 5).

The end cam 31 is accommodated together with the spring in the inner diameter portion of the boss portion 11, in order to prevent the separation of the threaded portion (11a) is formed on the outer periphery of the boss portion 11 to the spring and the end cam 31 And the screw cap 39 are coupled to the threaded portion 11a after being housed in the boss portion 11. The screw cap 39 has a through hole 40 formed therein so that the handle 38 of the driving cap 32 extends outward.

On the other hand, in order to prevent the deviation from the relative rotation between the drive cam 32 and the driven stem 33, the projection 41 is extended in the center of the drive cam 32, the cylindrical hole 42 formed in the center of the driven cam 33 By inserting in) guides the rotation of both cams (32, 33). On the other hand, at least one spline key (43) protrudes on the outer circumference thereof to prevent rotation of the driven cam (33), and the spline groove (corresponding to the spline key 43) on the inner diameter of the boss portion (11). 11b) is formed.

The operation of the embodiment of FIG. 5 will be described with reference to FIG.

In FIG. 6 (a), the two cams 32 and 33 constituting the end cam 31 have bushings B because their inclined surfaces 34 and 35 contact each other so that the distance between the two planes 36 and 37 is minimal. Only the minimum elastic force of the spring 12 is transmitted to minimize the grinding force.

As shown in FIG. 6 (b), when the knob 38 of the main cam 32 is rotated, the main cam 32 rotates relative to the driven cam 33 whose rotation is prevented by the spline key 43. The inclined surfaces 34 and 35 of the two cams 32 and 33 slide with each other, and thus the distance between the planes 36 and 37 of the two cams 32 and 33 increases. As a result, the spring 12 is compressed to press the bushing B with a larger force, thereby bringing the gap between the two grinding gears G1 and G2 into close contact with each other, thereby increasing the grinding force. In this embodiment, the handle 38 can be elastically maintained even in the intermediate state of FIGS. 6 (a) and 6 (b), so that the grinding force can be properly adjusted.

As described above, according to the present invention, even when the components of the green juice maker such as a grinding gear are manufactured with large tolerances to facilitate manufacturing, the gears can be brought into close contact with each other so that there is no gap between the grinding gears. In addition, when the gap between the grinding gears is increased due to wear due to use, it is possible to adjust appropriately, it is possible to provide the appropriate grinding force according to the type of material to be ground. In particular, the present invention can be pulverized to the fiber of the material that could not be pulverized with a conventional juice maker, it is possible to further improve the utility of the juice maker.

Claims (3)

And a pair of grinding gears G1 and G2 on which rotation shafts S11 to S22 of both ends are rotated and supported between the main body M including the driving unit and the housing H coupled to the main body M, respectively. Green juice provided with elastic crimping means 30 for elastically pushing the rotating shafts S11 to S22 of one of the grinding gears G1 or G2 among the grinding gears G1 and G2 to the other grinding gear G2 or G1 side. In the manufacturing machine, the elastic pressing means 30 is an end cam composed of a main cam 32 and a driven cam 33 each having inclined surfaces 34 and 35 in contact with each other and planes 36 and 37 on opposite sides thereof. Green juice maker characterized in that it comprises a (31). According to claim 1, wherein the pair of grinding gears (G1, G2) is composed of a main gear side G1 which is electrically coupled to the drive unit of the main body (M), and driven side gear (G2) driven by the tooth bite driven thereto. And the elastic pressing means (30) pushes the rotating shafts (S21, S22) of the driven side gear (G2) to the main side gear (G1) side. The green juice maker according to claim 1, wherein a bushing (B) made of a bearing material is provided on an outer circumference of the rotating shafts S11 to S22.