JP2014126001A - Compressor device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor device improved in compression efficiency while improving output efficiency.SOLUTION: A compressor device includes a piston 8 integrally provided with a piston head 7 on one end of a piston rod 6, and journaled to a crank pin 5P at the other end, a cylinder 10 forming a compression chamber 9 for compressing and sucking the air, with the piston head 7, a crank 5 capable of allowing a compressing motion of the piston head 7 in the cylinder 10 by a first half rotation of the crank pin 5P, and allowing an intake motion of the piston head 7 in the cylinder 10 by a remaining second half rotation of the crank pin 5P, and a ring seal 11 mounted on an outer periphery of the piston head 7. A rotation center h of the crank 5 is shifted in the direction to make the crank pin 5P exist in the second half rotation, with respect to a cylinder axis i, on a reference cross-section at a right angle to the rotation center h of the crank 5 through the cylinder axis i.

Description

The present invention relates to a compressor device. In particular, when a tire for an automobile is punctured, it is preferably used as a puncture repair kit that enables traveling by an emergency treatment by filling compressed air together with a sealing agent.

  As a compressor device for a tire puncture emergency repair kit, for example, the one described in Patent Document 1 below is known.

  FIG. 7 shows a compressor device described in Patent Document 1.

  This compressor device includes a piston 104 integrally provided with a piston head 103 at the other end of a piston shaft 102 whose one end is pivotally supported by a crankpin 101. A ring seal 106 that seals between the inner periphery of the cylinder 105 is disposed on the outer periphery of the piston head 103. As the crank 107 rotates, the piston 104 reciprocates between the bottom dead center and the top dead center while changing the piston angle Φ formed by the piston axis j and the cylinder axis i.

In this apparatus, the piston shaft 102 and the piston head 103 are integrally formed. Therefore, as the piston 104 reciprocates while changing the piston angle Φ, the ring seal 106 also reciprocates while changing the angle θ with respect to the plane X perpendicular to the cylinder axis i. Therefore, the projected outer diameter D1a when the outer diameter D1 of the ring seal 106 is projected onto the plane X changes according to the following equation (1).
D1a = D1 × cos θ (1)

  In this apparatus, the ring seal 106 is attached at a right angle to the piston axis j. For this reason, the angle θ is equal to the piston angle Φ. At the bottom dead center and the top dead center, the angle θ = Φ is 0 degree. At the intermediate point, the angle θ = Φ is the maximum value (θmax = Φmax). Therefore, the projected outer diameter D1a is maximum (= D1) at the bottom dead center and top dead center, and is minimum (= D1 × cos θmax) at the intermediate point. Then, the maximum change amount ΔD0 of the projected outer diameter D1a is ΔD0 = D1 × (1−cos θmax).

  On the other hand, in the compressor device, when the piston 104 reciprocates, it is necessary to bring the ring seal 106 and the inner peripheral surface of the cylinder 105 into airtight contact. Therefore, the ring seal 106 needs to be further subjected to elastic deformation for absorbing the above-described maximum change amount ΔD, in addition to elastic deformation for airtight contact.

  However, when the total elastic deformation amount of the ring seal 106 increases, the deformation resistance of the ring seal 106 also increases. As a result, the current value of the drive motor (DC motor) increases to lower the output efficiency, and the compressor performance decreases accordingly. In addition, when trying to ensure airtightness with the cylinder 105 in a state where the total amount of elastic deformation of the ring seal 106 is large, the selection of the material constituting the ring seal 106 and the accuracy of the ring seal itself become severe, which is costly. Will bounce off.

  Therefore, a compressor device described in Patent Document 2 below is devised and provided.

  FIG. 8 shows a compressor device described in Patent Document 2.

This device is a compressor device having a piston 104 in which a piston shaft 102 and a piston head 103 are integrally formed. In a reference cross section perpendicular to the rotation center h of the crank 107 through the cylinder axis i, the ring seal 106 is mounted inclined at an angle α with respect to a reference line X perpendicular to the piston axis j. The angle α is in a range of 0.3 to 0.7 times the maximum value Φmax of the piston angle Φ formed by the piston axis j and the cylinder axis i when the piston head 103 reciprocates. . In this way, the amount of change in the projected outer diameter of the ring seal 106 is reduced and the increase in the value of the current flowing through the drive motor is suppressed during the compression stroke in which the motor load increases.

JP 2005-344570 A JP 2012-154260 A

  In the compressor device described in Patent Document 2, the rotation center h of the crank 107 overlaps the cylinder axis i. The piston 104 is reciprocated by the crank 107 rotating in this state. The ring seal 106 is attached to the reference line X at an angle α. Furthermore, the angle α is set to 0.3 to 0.7 times the maximum value Φmax of the piston angle Φ. The optimum value of the angle α is 0.5 times Φmax.

In such a structure, in order to increase the compression rate by increasing the stroke of the piston 104, the maximum value Φmax of the piston angle Φ must be increased accordingly. Of course, the angle α needs to be increased in proportion thereto. When the maximum value Φmax of the piston angle Φ and the angle α for inclining the ring seal 106 are increased more than necessary, the piston angle Φ is the maximum value (Φmax) at the midpoint between the top dead center and the bottom dead center. The inclination angle of the ring seal 106 becomes excessive, and airtightness between the cylinder 105 and the ring seal 106 cannot be ensured. Therefore, there is a limit in increasing the stroke of the piston 104, and the compression efficiency cannot be increased by increasing the compression rate beyond a certain level.

The present invention has been made to solve the above-described problem, and is a compressor device capable of increasing the compression rate and improving the compression efficiency while suppressing the increase in the current value flowing through the drive motor and improving the output efficiency. The purpose is to provide.

In order to achieve the above object, a compressor apparatus of the present invention includes a piston having a piston head integrally provided at one end of a piston rod and the other end pivotally supported by a crank pin,
A cylinder in which the piston head is accommodated so as to be able to reciprocate on the cylinder axis i and forms a compression chamber for compressing and sucking air with the piston head;
The crank pin is rotated around its rotation center h by being driven to rotate, and the piston pin can be compressed in the cylinder by the first half rotation of the crank pin, and the remaining second half rotation of the crank pin A crank that enables the intake motion of the piston head in the cylinder;
A ring seal attached to the outer periphery of the piston head and sealing between the inner peripheral surface of the cylinder;
In a reference cross section perpendicular to the rotation center h of the crank through the cylinder axis i,
The gist of the center of rotation h of the crank is that the crank pin is arranged at a position shifted from the cylinder axis i in the direction of the second half rotation.

According to the present invention, in the reference cross section perpendicular to the crank rotation center h through the cylinder axis i, the crank rotation center h is such that the crank pin is in the second half rotation with respect to the cylinder axis i. It is arranged at a position shifted in the existing direction.
When the crank is driven to rotate, the piston head reciprocates in the cylinder. In the first half rotation in which the piston head performs a compression motion, the crank pin moves in an arc in a region near the cylinder axis i. On the other hand, in the second half rotation in which the piston head performs an intake motion, the crank pin moves in a circular arc in a region far from the cylinder axis i. Therefore, when the piston head performs a compression movement, the angle formed by the piston axis j and the cylinder axis i is smaller than that during the intake movement. As a result, the angle of inclination of the ring seal with respect to the cylinder axis i when reciprocating in the cylinder is reduced particularly during the compression movement.

  For this reason, in this invention, the deformation resistance of the ring seal at the time of compression movement can be suppressed small. Therefore, the output efficiency can be secured by suppressing the current value of the drive motor. In addition, the selection of the material constituting the ring seal and the accuracy of the ring seal itself do not become more severe than necessary, so that an increase in cost can be avoided. Furthermore, it is easy to ensure airtightness between the cylinder and the ring seal during the compression movement, and it is possible to increase the compression rate and increase the compression efficiency.

In the present invention, when the displacement amount of the crank rotation center h with respect to the cylinder axis i is less than 50% of the stroke in the reciprocating motion of the piston head,
Particularly during the compression movement, the inclination angle of the ring seal with respect to the cylinder axis i when reciprocating in the cylinder becomes small. In addition, during the intake motion, the inclination angle of the ring seal with respect to the cylinder axis i can be suppressed within a range that does not become excessive.

In the present invention, when the displacement amount of the crank rotation center h with respect to the cylinder axis i is 20% or more and less than 30% of the stroke in the reciprocating motion of the piston head,
Particularly during the compression movement, the inclination angle of the ring seal with respect to the cylinder axis i when reciprocating in the cylinder becomes small. In addition, during the intake motion, the inclination angle of the ring seal with respect to the cylinder axis i can be suppressed within a range that does not become excessive.

In the present invention, when the ring seal is mounted substantially parallel to a reference line X perpendicular to the piston axis j,
Particularly during the compression movement, the inclination angle of the ring seal with respect to the cylinder axis i when reciprocating in the cylinder becomes small. In addition, during the intake motion, the inclination angle of the ring seal with respect to the cylinder axis i can be suppressed within a range that does not become excessive.
Further, since the design and production of the piston are not complicated as in the conventional example, an increase in design cost and production cost can be suppressed.

It is a perspective view which shows the whole structure of the compressor apparatus in 1st Embodiment of this invention. It is a disassembled perspective view which shows a compressor main body. It is a figure explaining the principal part and operation | movement of the compressor main body 3. FIG. It is a figure explaining the principal part and operation | movement of the compressor main body 3. FIG. It is a figure explaining the principal part and operation | movement of the compressor main body 3. FIG. It is a figure explaining the principal part and operation | movement of the compressor main body 3. FIG. This is a compressor device described in Patent Document 1. This is a compressor device described in Patent Document 2.

  Hereinafter, embodiments of the compressor device of the present invention will be described in detail.

  FIG. 1 is a diagram illustrating an overall structure of a compressor device 1 according to the present embodiment.

  The compressor device 1 according to the present embodiment includes a drive motor M and a compressor body 3 driven by the drive motor M in a storage case 2.

  As the drive motor M, various commercially available DC motors that operate with a 12V DC power source of an automobile can be employed. A power cord 4 having a power plug 4A that can be connected to a cigarette lighter socket of an automobile is connected to the drive motor M via a power switch SW attached to the upper surface of the storage case 2.

  FIG. 2 is a view showing the compressor body 3.

  The compressor body 3 can reciprocate a crank 5 that is rotationally driven by a drive motor M, a piston 8 having one end attached to a crank pin 5P of the crank 5, and a piston head 7 provided at the other end of the piston 8. A cylindrical cylinder 10 accommodated in the piston head 7 and a ring seal 11 attached to the outer periphery of the piston head 7 are provided.

  The piston 8 is integrally provided with a piston head 7 at one end of a piston rod 6 and the other end is pivotally supported by a crank pin 5P. In this example, the piston head 7 is formed in a cylindrical shape. In this example, the piston 8 is formed as an integrally molded product made of FRP (fiber reinforced plastic).

  The cylinder 10 is a cylindrical body having a cylinder axis i. The piston head 7 is accommodated so as to reciprocate on the cylinder axis i. In this state, a compression chamber 9 (see FIGS. 3 to 6) that compresses and sucks air is formed between the piston head 7 and the cylinder 10. As the crank 5 rotates once, the piston head 7 reciprocates between the bottom dead center and the top dead center on the cylinder axis i.

  The crank 5 is driven to rotate about a rotation center h by a drive motor M connected via a known speed reduction mechanism 12 using, for example, a gear or a pulley. The crank 5 is provided with a crank pin 5P at a position separated from the rotation center h. Therefore, when the crank 5 is driven to rotate, the crank pin 5P rotates around the rotation center h and moves around.

  Then, the piston head 7 can be compressed in the cylinder 10 by the first half rotation of the crank pin 5P. The first half rotation is a half rotation of the crank 5 in which the piston head 7 moves from the bottom dead center toward the top dead center in the cylinder 10. Further, the second half rotation of the crank pin 5P allows the piston head 7 to perform an intake motion within the cylinder 10. The second half rotation is a half rotation of the crank 5 in which the piston head 7 moves from the top dead center toward the bottom dead center in the cylinder 10.

  The ring seal 11 is attached to the outer periphery of the piston head 7 and seals between the inner peripheral surface of the cylinder 10. The ring seal 11 is made of, for example, a rubber elastic material such as nitrile rubber (NBR), hydrogenated nitrile rubber (HNBR), silicon rubber (Q), or fluorine rubber (FKM). The ring seal 11 is fitted into a circumferential groove provided on the outer periphery of the piston head 7.

  An intake / exhaust valve unit 13 is attached to the head portion of the cylinder 10. The intake / exhaust valve unit 13 includes an exhaust valve and an intake valve (not shown). The exhaust valve exhausts the compressed air when the piston head 7 is compressed in the cylinder 10 and the air is compressed in the compression chamber 9. The intake valve sucks air into the compression chamber 9 from the outside when the piston head 7 performs an intake motion in the cylinder 10. In the figure, reference numeral 14 denotes a compressed air supply hose 14 which is connected to the nipple 15 of the intake / exhaust valve unit 13.

  3-6 is a figure explaining the principal part and operation | movement of the said compressor main body 3. As shown in FIG.

FIG. 3 shows a state where the piston head 7 is located at the bottom dead center.
FIG. 4 shows a state in which the piston head 7 is compressed from the bottom dead center toward the top dead center.
FIG. 5 shows a state where the piston head 7 is located at the top dead center.
FIG. 6 shows a state in which the piston head 7 performs an intake motion from the top dead center toward the bottom dead center.

  In this embodiment, a reference cross section perpendicular to the rotation center h of the crank 5 through the cylinder axis i is set.

  3 to 6 are sectional views of the reference section. In the cross-sectional view of the reference cross section, the crank 5 rotates leftward about the rotation center h. By rotating the crank 5 once, the piston head 7 is moved from bottom dead center (FIG. 3) to compression motion (FIG. 4) to top dead center (FIG. 5) to intake motion (FIG. 6) to bottom dead center (FIG. 3). And exercise. Therefore, from the bottom dead center (FIG. 3) to the compression motion (FIG. 4) to the top dead center (FIG. 5), the piston head 7 moves from the bottom dead center toward the top dead center in the cylinder 10. Half turn. From the top dead center (FIG. 5) to the intake motion (FIG. 6) to the bottom dead center (FIG. 3), the second half rotation in which the piston head 7 moves from the top dead center toward the bottom dead center in the cylinder 10 It is.

  In the present embodiment, the rotation center h of the crank 5 is arranged at a position shifted in the direction in which the crank pin 5P exists in the second half rotation with respect to the cylinder axis i. In the cross-sectional view of the reference cross section, it is the left side of the drawing with respect to the cylinder axis i.

  Since the crank pin 5P is disposed at a position shifted in the direction of the second half rotation with respect to the cylinder axis i, at the position where the piston head 7 becomes the bottom dead center (FIG. 3), the cylinder shaft The piston axis j is inclined with respect to the center i at an angle α0.

  In this example, the top surface 16 of the piston head 7 is formed along a reference line X perpendicular to the piston axis j. That is, the top surface 16 of the piston head 7 is perpendicular to the piston axis j. The ring seal 11 is mounted substantially parallel to a reference line X perpendicular to the piston axis j. Here, the piston axis j is an axis passing through the center of the crank pin 5P from the center of the piston head 7 in the reference cross section described above.

  In this state, the top surface 16 of the piston head 7 is inclined at an angle α0 with respect to a plane orthogonal to the cylinder axis i. Similarly, the ring seal 11 is also inclined at an angle α0 with respect to a plane orthogonal to the cylinder axis i.

  FIG. 4 shows a state where the crank 5 rotates from the state shown in FIG. 3 and the piston head 7 performs a compression motion. FIG. 4 shows a state where the crank 5 is rotated 90 ° from the bottom dead center and the piston head 7 is positioned between the bottom dead center and the top dead center. The angle α formed by the cylinder axis i with respect to the piston axis j is smaller than the bottom dead center which is the initial state. Accordingly, the angle α formed by the top surface 16 of the piston head 7 and the ring seal 11 with respect to the surface orthogonal to the cylinder axis i is also reduced.

  Thus, the compression operation is performed in a state where the angle α formed by the ring seal 11 with respect to the plane orthogonal to the cylinder axis i is small. For this reason, the deformation resistance of the ring seal 11 during the compression movement can be kept small. Therefore, the output efficiency can be ensured by suppressing the current value of the drive motor M. In addition, the selection of the material constituting the ring seal 11 and the accuracy of the ring seal 11 itself do not become more severe than necessary, so an increase in cost can be avoided. Furthermore, it is easy to ensure airtightness between the cylinder 10 and the ring seal 11 during the compression motion, and it is possible to increase the compression rate and increase the compression efficiency.

  FIG. 5 shows a state where the crank 5 is further rotated from the state shown in FIG. 4 and the piston head 7 is located at the top dead center. In this state, the angle α formed by the piston axis j with respect to the cylinder axis i is the same as the state where the piston head 7 is located at the bottom dead center. Therefore, in this state, the top surface 16 of the piston head 7 is inclined at an angle α0 with respect to a plane orthogonal to the cylinder axis i.

  In this example, the ceiling surface 17 constituting the compression chamber 9 of the cylinder 10 is inclined at an angle α0 with respect to a plane orthogonal to the cylinder axis i. Therefore, the top surface 16 of the piston head 7 and the ceiling surface 17 of the cylinder 10 are parallel with the piston head 7 positioned at the top dead center. In this state, the compression efficiency can be ensured by reducing the volume of the compression chamber 9 to the limit.

  FIG. 6 shows a state where the crank 5 further rotates from the state of FIG. 5 and the piston head 7 performs an intake motion. FIG. 6 shows a state in which the crank 5 is rotated 90 ° from the top dead center and the piston head 7 is positioned between the top dead center and the bottom dead center. Thereafter, the crank 5 further rotates to return to the state shown in FIG.

Here, the amount of deviation of the rotation center h of the crank 5 from the cylinder axis i is preferably less than 50% of the stroke in the reciprocating motion of the piston head 7.
Furthermore, the amount of deviation of the rotation center h of the crank 5 from the cylinder axis i is preferably 20% or more and less than 30% of the stroke in the reciprocating motion of the piston head 7.
By doing so, the inclination angle of the ring seal 11 with respect to the cylinder axis i when reciprocating in the cylinder 10 is reduced particularly during the compression movement. In addition, during the intake motion, the inclination angle of the ring seal 11 with respect to the cylinder axis i can be suppressed within a range in which it does not become excessive.

The ring seal 11 is preferably mounted substantially parallel to the reference line X perpendicular to the piston axis j.
By doing so, the inclination angle of the ring seal 11 with respect to the cylinder axis i when reciprocating in the cylinder 10 is reduced particularly during the compression movement. In addition, during the intake motion, the inclination angle of the ring seal 11 with respect to the cylinder axis i can be suppressed within a range in which it does not become excessive.
Moreover, since the design and production of the piston 8 are not complicated as in the conventional example, an increase in design cost and production cost can be suppressed.

As described above, the compressor apparatus 1 of the present embodiment is configured such that the rotation center h of the crank 5 is relative to the cylinder axis i in the reference cross section perpendicular to the rotation center h of the crank 5 through the cylinder axis i. Thus, the crank pin 5P is arranged at a position shifted in the direction existing in the second half rotation.
When the crank 5 is driven to rotate, the piston head 7 reciprocates in the cylinder 10. In the first half rotation in which the piston head 7 performs a compression motion, the crankpin 5P moves in an arc in a region near the cylinder axis i. On the other hand, in the second half rotation in which the piston head 7 performs the intake motion, the crank pin 5P moves in an arc in a region far from the cylinder axis i. Therefore, when the piston head 7 performs a compression movement, the angle formed by the piston axis j and the cylinder axis i is smaller than that during the intake movement. As a result, the angle of inclination of the ring seal 11 with respect to the cylinder axis i when reciprocating in the cylinder 10 is reduced particularly during the compression movement.

  For this reason, in this embodiment, the deformation resistance of the ring seal 11 during the compression motion can be kept small. Therefore, the output efficiency can be secured by suppressing the current value of the drive motor. In addition, the selection of the material constituting the ring seal 11 and the accuracy of the ring seal 11 itself do not become more severe than necessary, so an increase in cost can be avoided. Furthermore, it is easy to ensure airtightness between the cylinder 10 and the ring seal 11 during the compression motion, and it is possible to increase the compression rate and increase the compression efficiency.

The above has described a particularly preferred embodiment of the present invention. However, the present invention is not intended to be limited to the illustrated embodiment, and can be implemented by being modified into various aspects. The present invention includes various modifications. This is the purpose.

1: Compressor device 2: Storage case 3: Compressor body 4: Power cord 4A: Power plug 5: Crank 5P: Crank pin 6: Piston rod 7: Piston head 8: Piston 9: Compression chamber 10: Cylinder 11: Ring seal 12 : Deceleration mechanism 13: Intake / exhaust valve unit 14: Hose 15: Nipple 16: Top surface 17: Ceiling surface M: Drive motor SW: Power switch h: Center of rotation i: Cylinder shaft center j: Piston shaft center 101: Crank pin 102 : Piston shaft 103: Piston head 104: Piston 105: Cylinder 106: Ring seal 107: Crank

Claims (4)

A piston head integrally provided at one end of the piston rod and the other end pivotally supported by a crankpin;
A cylinder in which the piston head is accommodated so as to be able to reciprocate on the cylinder axis i and forms a compression chamber for compressing and sucking air with the piston head;
The crank pin is rotated around its rotation center h by being driven to rotate, and the piston pin can be compressed in the cylinder by the first half rotation of the crank pin, and the remaining second half rotation of the crank pin A crank that enables the intake motion of the piston head in the cylinder;
A ring seal attached to the outer periphery of the piston head and sealing between the inner peripheral surface of the cylinder;
In a reference cross section perpendicular to the rotation center h of the crank through the cylinder axis i,
The compressor device according to claim 1, wherein the crank rotation center h is disposed at a position shifted in a direction in which the crank pin exists in the second half rotation with respect to a cylinder axis i.   2. The compressor apparatus according to claim 1, wherein the amount of deviation of the crank rotation center h with respect to the cylinder axis i is less than 50% of the stroke in the reciprocating motion of the piston head.   The compressor apparatus according to claim 2, wherein a displacement amount of the rotation center h of the crank with respect to the cylinder axis i is 20% or more and less than 30% of a stroke in the reciprocating motion of the piston head.   The compressor device according to any one of claims 1 to 3, wherein the ring seal is mounted substantially parallel to a reference line X perpendicular to the piston axis j.

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