JP2012154260A - Compressor device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce a change amount in a projective outer diameter of a ring seal and suppress an increase in a value of current flowing through a drive motor, on a compression stroke during which a load of the drive motor is large.SOLUTION: In a compressor device 1 including a piston 8 integrally formed with a piston shaft 6 and a piston head 7, a ring seal 11 is attached to be inclined at an angle α with respect to a reference line X perpendicular to a piston axis j, in a reference cross section passing through a cylinder axis i and perpendicular to a rotation center h of a crank 5. The angle α is within a range of 0.3 to 0.7 times of a maximum value Φof a piston angle Φ formed between the piston axis j and the cylinder axis i when the piston head 7 reciprocates.

Description

  The present invention relates to a compressor device that can be suitably used for a tire puncture emergency repair kit that enables filling of compressed air together with a sealing agent and enables an emergency running of a tire, particularly when the tire is punctured.

  As a compressor device for a tire puncture emergency repair kit, for example, the one described in Patent Document 1 is known. As conceptually shown in FIG. 10 (A), this compressor apparatus includes a piston b integrally provided with a piston head b2 at the other end of a piston shaft b1 whose one end is pivotally supported by a crankpin a. A ring seal d is disposed on the outer periphery of the piston head b2 to seal the space between the inner periphery of the cylinder c. As the crank e rotates, the piston b reciprocates between the bottom dead center PL and the top dead center PU while changing the piston angle Φ formed by the piston axis j and the cylinder axis i.

At this time, since the piston shaft b1 and the piston head b2 are integrally formed, the ring seal d also reciprocates while changing the angle θ with respect to the plane Y perpendicular to the cylinder axis i. That is, as shown in FIG. 10B, the projected outer diameter D1a when the outer diameter D1 of the ring seal d is projected onto the plane Y changes according to the following equation.
D1a = D1 × cos θ

Here, conventionally, since the ring seal d is mounted at a right angle with respect to the piston axis j, the angle θ is equal to the piston angle Φ, and the angle at the bottom dead center PL and the top dead center PU. θ (= Φ) is 0 degree, and the maximum value θmax (= Φmax) is formed at the intermediate point PM. Therefore, the projected outer diameter D1a is maximum (= D1) at the bottom dead center PL and the top dead center PU, and is minimum (= D1 × cos θmax) at the intermediate point PM. That is, the maximum change amount ΔD ₀ of the projected outer diameter D1a is ΔD ₀ = D1 × (1−cos θmax).

  On the other hand, in the compressor device, when the piston b reciprocates, the ring seal d and the inner peripheral surface of the cylinder c need to be in airtight contact. Therefore, the ring seal d has elastic deformation for airtight contact. In addition, it is necessary to further elastically deform in order to absorb the maximum change amount ΔD.

  However, when the total elastic deformation amount increases, the deformation resistance of the ring seal d also increases. As a result, the current value of the drive motor (DC motor) increases, resulting in a problem that the output efficiency is lowered, that is, the compressor performance is lowered.

JP 2005-344570 A

Therefore, the present invention is based on the fact that the ring seal is inclined at a predetermined angle α with respect to the reference line X perpendicular to the piston axis, and the projected outer diameter of the ring seal is reduced during the compression stroke in which the load of the drive motor becomes large. The amount of elastic deformation of the ring seal can be kept low by reducing the maximum amount of change,
An object of the present invention is to provide a compressor device capable of suppressing an increase in the value of a current flowing through a drive motor and improving output efficiency.

In order to solve the above problems, the invention of claim 1 of the present application includes a crank having a crankpin that is driven to rotate by a motor and circulates around its rotation center h.
A piston integrally provided with a piston head at the other end of the piston shaft pivotally supported at one end by the crank pin;
It has a cylinder axis i passing through the rotation center h, and accommodates the piston head in a reciprocable manner from the bottom dead center to the top dead center on the cylinder axis i and air between the piston head A cylindrical cylinder that forms a pump chamber to compress,
A compressor device comprising a ring seal that attaches to the outer periphery of the piston head and seals between the inner peripheral surface of the cylinder;
In a reference cross section perpendicular to the rotation center h through the cylinder axis i, the ring seal is attached at an angle α with respect to a reference line X perpendicular to the piston axis j, and
The angle α is 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 reciprocates. .

  According to a second aspect of the present invention, the ring seal is inclined at an angle α from the reference line X in a direction opposite to the rotation direction around the rotation center h of the crank.

  As described above, in the present invention, the ring seal is mounted at an angle α with respect to a reference line X perpendicular to the piston axis j in a reference cross section perpendicular to the rotation center h through the cylinder axis i. Yes. Moreover, the angle α is set to 0.3 to 0.7 times the maximum value Φmax of the piston angle Φ when the piston head reciprocates. As a result, for the reason described in the “Mode for Carrying Out the Invention” section below, the maximum amount of change in the projected outer diameter of the ring seal can be reduced in the compression stroke in which the load of the drive motor becomes large. As a result, the deformation resistance of the ring seal in the compression stroke can be kept low, and an increase in the value of the current flowing through the drive motor can be suppressed, and the output efficiency can be improved.

It is a perspective view which shows one Example of the compressor apparatus of this invention. It is a disassembled perspective view which shows the principal part. It is sectional drawing which shows the principal part. (A), (B) is sectional drawing of a ring seal, and its partial enlarged view. It is sectional drawing which shows the attachment angle (alpha) of a ring seal. It is a conceptual diagram which shows the motion of 1 cycle of a piston. It is a conceptual diagram explaining the movement of a ring seal. It is a graph which shows the change of the projection outer diameter of a ring seal as a parameter with the attachment angle (alpha) of a ring seal. (A) is a graph which shows the change of the projection outer diameter of the ring seal in the example goods at the time of normal temperature and low temperature, (B) is a graph which shows a clearance gap formation state. (A), (B) is a conceptual diagram explaining operation | movement of the conventional compressor apparatus.

Hereinafter, embodiments of the present invention will be described in detail.
In FIG. 1, the compressor device 1 of 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 motor M, various commercially available DC motors that operate with a 12V DC power source of an automobile can be used. A power cord 4 having a power plug 4 </ b> A that can be connected to a cigarette lighter socket of an automobile is connected to the drive motor M via a power switch SW that is attached to the upper surface of the storage case 2.

  Next, as shown in FIG. 2, the compressor body 3 includes a crank 5 that is rotationally driven by a drive motor M, and a piston at the other end of a piston shaft 6 that is pivotally supported by a crank pin 5 </ b> P of the crank 5. A piston 8 provided integrally with the head 7, a cylindrical cylinder 10 that accommodates the piston head 7 so as to reciprocate from a bottom dead center PL to a top dead center PU, and a ring seal that is attached to the outer periphery of the piston head 7. 11 and.

  The crank 5 is rotated around a rotation center h by a drive motor M connected via a known speed reduction mechanism 12 using, for example, a gear, a pulley, or the like. As is well known, the crank 5 is provided with a crank pin 5P at a position separated from the rotation center h. Therefore, the crank pin 5P moves around the rotation center h.

  The piston 8 includes a piston shaft 6 whose one end is pivotally supported by the crank pin 5P, and a cylindrical piston head 7 is integrally formed at the other end of the piston shaft 6. In this example, the case where the piston 8 is formed as an integrally molded product made of FRP (fiber reinforced plastic) is shown. As shown in FIGS. 2 and 3, the piston head 7 has an intake hole 13A extending through the piston head 7 in the axial direction of the piston, and the intake hole 13A has a spring property from the upper surface side of the piston. The intake valve 13 is formed using a valve body 13B such as an elastic body such as rubber, synthetic resin, or metal.

  The cylinder 10 is a cylindrical body having a cylinder axis i passing through the rotation center h, and the piston head 7 can reciprocate from the bottom dead center PL to the top dead center PU on the cylinder axis i. And a pump chamber 14 for compressing air with the piston head 7 is formed.

  The cylinder 10 is provided with air supply means 15 having an air supply passage 15A for supplying compressed air from the pump chamber 14 to the outside of the apparatus. The air supply means 15 includes a surge tank portion 17 having a surge tank chamber 17A connected to the pump chamber 14 via an inflow port 16. The surge tank chamber 17A stores the compressed air from the pump chamber 14 and suppresses pressure pulsation caused by the piston. A check valve can be provided at the inlet 16. The surge tank 17 is provided with, for example, a nipple-shaped connecting portion 19 for detachably connecting a compressed air feeding hose 18, and the air feeding means 15 is connected to the surge tank 17. And the hose 18.

  The ring seal 11 is made of a rubber elastic material such as nitrile rubber (NBR), hydrogenated nitrile rubber (HNBR), silicon rubber (Q), or fluorine rubber (FKM), and is provided on the outer periphery of the piston head 7. Fit into the groove 7A. Specifically, in this example, the ring seal 11 is formed by forming a V-shaped groove 21 in the upper part of the base 20 having a substantially rectangular cross section as shown in FIGS. 4 (A) and 4 (B). On both sides of the V-shaped groove, an outer lip piece 20a inclined radially outwardly upward and an inner lip piece 20b inclined radially inward are formed in a V-shaped cross section. . Such a ring seal 11 can be suitably employed in the compressor device 1 of the present embodiment because the outer lip piece 20a can be easily elastically deformed radially inward. For convenience, in FIGS. 3, 5, 6, and 7, the ring seal 11 is drawn in a circular cross section.

  In the present invention, as shown in FIG. 5, in the reference cross section perpendicular to the rotation center h through the cylinder axis i, the ring seal 11 is in relation to the reference line X perpendicular to the piston axis j. Mounted at an angle α. In this example, the piston head 7 itself is inclined at an angle α with respect to the reference line X, and the ring seal 11 is attached concentrically with the inclined piston head 7. The ring seal 11 is inclined from the reference line X in the direction opposite to the rotation direction of the crank 5 around the rotation center h. Specifically, in this example, the crank 5 rotates clockwise around the rotation center h, and the ring seal 11 is inclined from the reference line X counterclockwise by an angle α. This angle α is set 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 reciprocates. .

  6 conceptually shows the movement of the piston 8 in one cycle, when the crank 5 rotates, the piston 8 reciprocates while changing the piston angle Φ formed by the piston axis j and the cylinder axis i. Move. At this time, in the coordinate system in which the crank rotation angle ω at the bottom dead center PL is set to 0 ° (referenced to the bottom dead center PL), the piston angle Φ is set to 0 ° and 180 ° as in the conventional art. The position (the position of the bottom dead center PL and the top dead center PU) is 0 ° (Φ = 0 °), and the crank rotation angle ω is 90 ° (compression side intermediate position PM1) and 270 ° (intake side intermediate). At the position PM2), the piston angle Φ has a maximum value Φmax and a minimum value Φmin, respectively. The piston angle Φ is positive on the compression stroke side and negative on the intake stroke side.

On the other hand, the ring seal 11 also reciprocates while changing the angle θ with respect to the plane Y perpendicular to the cylinder axis i as shown in FIG. However, in the case of the present invention, the ring seal 11 is inclined at an angle α from the reference line X in the direction opposite to the rotation direction of the crank 5. Accordingly, the angle θ is expressed by the following formula (1), and the projected outer diameter D1a when the outer diameter D1 of the ring seal 11 is projected onto the plane Y is expressed by the following formula (2).
θ = Φ−α −−− (1)
D1a = D1 × cos (Φ−α) −−− (2)

Accordingly, in the compression stroke (ω = 0 ° to 180 °), the projected outer diameter D1a is {D1 × cos (−α)} → {D1 × cos (0)} → {D1 × cos (θmax−α). } → {D1 × cos (0)} → {D1 × cos (α)}. When α ≦ θmax / 2, the maximum change amount of the projected outer diameter is ΔD = D1 × {1-cos (θmax−α)}, and when α ≧ θmax / 2, the maximum change amount of the projected outer diameter. Is ΔD = D1 × (1−cos α). In any case, the maximum change amount ΔD of the projected outer diameter is smaller than the conventional maximum change amount ΔD ₀ = D1 × (1−cos θmax).

  In particular, when the angle α is 0.5 times the maximum value Φmax (α = θmax / 2), the maximum change amount ΔD of the projected outer diameter is minimum, which is most preferable. However, the maximum value Φmax is 0.3 to Even in the range of 0.7 times, the effect of reducing the maximum change amount ΔD can be sufficiently exerted, so that it can be employed.

FIG. 8 shows the change in the projected outer diameter D1a of the ring seal 11 per piston cycle, using the angle α as a parameter. In this example, the maximum value Φmax of the piston angle Φ is 11.2 °. As shown in FIG. 8, in the compression stroke (ω = 0 ° to 180 °), the angle α is 3.36 ° to 7.84 ° (the maximum value Φmax of the piston angle Φ is 0.3 to 0. 0). It is confirmed that the maximum change amount ΔD of the projected outer diameter can be greatly reduced compared to the maximum change amount ΔD ₀ in the conventional product (α = 0 °).

Therefore, in the compression stroke in which the load of the drive motor M becomes large, the elastic deformation amount of the ring seal 11 can be minimized while the ring seal 11 is brought into airtight contact with the inner peripheral surface of the cylinder 10. It is possible to reduce the load on the motor to reduce the power consumption and improve the output efficiency of the drive motor.

In the compressor apparatus 1 of the present embodiment, as shown in FIG. 8 above, during the intake stroke (ω = 180 ° to 360 °), the maximum change amount ΔD of the projected outer diameter is, conversely, the projected outer diameter of the conventional product. It increases in comparison with the amount of change [Delta] D _0. That is, in the intake stroke, the projected outer diameter D1a is small, and a gap is generated between the ring seal 11 and the inner peripheral surface of the cylinder 10. However, there is no problem in the intake stroke because air is supplied into the pump chamber 14.

  Next, the relationship between the projected outer diameter D1a of the ring seal 11 and the inner diameter D0 of the cylinder 10 will be described. As shown in FIG. 9A, at least at normal temperature (20 ° C.), the projected outer diameter D1a of the ring seal 11 in the compression stroke needs to be larger than the inner diameter D0 of the cylinder 10, Thus, the ring seal 11 can be brought into airtight contact with the cylinder 10, and air can be compressed in the pump chamber 14.

  However, at this time, if the difference (D1a−D0) between the projected outer diameter D1a and the inner diameter D0 at the normal temperature (20 ° C.), that is, the overlap amount δ, which is the elastic deformation amount of the ring seal 11, is too large. The effect of improving the output efficiency of the motor is not achieved sufficiently, and when used in a low temperature state (for example, −40 ° C.), the load on the drive motor M at the time of start-up becomes large and the fuse is blown out. Invite the fear to occur.

  That is, when used in the low temperature state, the inner diameter D0 of the cylinder 10 made of a metal material hardly changes, but the ring seal 11 made of a rubber elastic material contracts to reduce the projected outer diameter D1a. Therefore, as shown in FIG. 9A, the overlap amount δ itself is small in the low temperature state, but the ring seal 11 itself is cured by the low temperature, so that the load on the drive motor M at the time of startup is reduced. On the other hand, it may become large and cause a blown fuse. 9A shows the projected outer diameter D1a of the ring seal 11 and the cylinder at normal temperature (20 ° C.) when the angle α of the ring seal 11 is 5.6 ° (α = θmax / 2). An inner diameter D0 of 10, a projected outer diameter D1a of the ring seal 11 at −40 ° C., and an inner diameter D0 of the cylinder 10 are shown. In the case of the figure, the inner diameter D0 of the cylinder 10 at the normal temperature is 17.7 mm, the inner diameter decreases toward the top dead center PU due to a draft of about 3 °, and the ring seal at the normal temperature. 11 has an outer diameter D1 of 18.3 mm.

  Therefore, as shown in FIG. 9B, at least the normal temperature (20 ° C.), the projection outer diameter D1a in the compression stroke is made larger than the inner diameter D0 of the cylinder 10, and the overlap amount δ is set lower. Thus, in the low temperature state, the projected outer diameter D1a in the compression stroke is set to be equal to or smaller than the inner diameter D0 of the cylinder 10, and a minute gap G (including the case where G = 0 mm) is provided between the ring seal 11 and the cylinder 10. It is preferable to form. Although FIG. 9B shows a case where the minute gap G is formed over the entire compression stroke, the minute gap G may be formed in at least a part of the compression stroke. In other words, at a normal temperature (20 ° C.), while the projection outer diameter D1a in the compression stroke is larger than the inner diameter D0 of the cylinder 10, the ring seal 11 and the cylinder 10 are It is preferable to set the overlap amount δ at a normal temperature (20 ° C.) so low that the minute gap G is formed between the two.

  When the minute gap G is formed in this way, the deformation resistance of the ring seal 11 can be kept low at the time of startup, so the load on the drive motor M can be reduced and the current value at the time of low temperature startup can be reduced. The temperature in the low temperature state is preferably selected from the range of -30 to -40 ° C.

  Here, the maximum value Gmax of the gap G is preferably larger than 0 mm and not larger than 1.0 mm. When the maximum value Gmax is 1.0 mm or less, as shown in FIG. 9 (B), the ring seal 11 is thermally expanded in the normal temperature state and closes the gap G over the entire compression stroke. That is, the ring seal 11 can be brought into airtight contact with the inner peripheral surface of the cylinder 10. However, if the maximum value Gmax exceeds 1.0 mm, the gap G is not blocked even at normal temperature, and the compressor performance may be reduced. Therefore, the lower limit value of the maximum value Gmax is preferably 0.3 mm or more, and the upper limit value is preferably 0.5 mm or less.

  As mentioned above, although especially preferable embodiment of this invention was explained in full detail, this invention is not limited to embodiment of illustration, It can deform | transform and implement in a various aspect.

1 Compressor 5 Crank 5P Crankpin 6 Piston shaft 7 Piston head 8 Piston 10 Cylinder 11 Ring seal 14 Pump chamber G Clearance M Motor PL Bottom dead center PU Top dead center

Claims (2)

A crank having a crankpin that is driven to rotate by a motor and circulates around its rotation center h;
A piston integrally provided with a piston head at the other end of the piston shaft pivotally supported at one end by the crank pin;
It has a cylinder axis i passing through the rotation center h, and accommodates the piston head in a reciprocable manner from the bottom dead center to the top dead center on the cylinder axis i and air between the piston head A cylindrical cylinder that forms a pump chamber to compress,
A compressor device comprising 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 through the cylinder axis i, the ring seal is attached at an angle α with respect to a reference line X perpendicular to the piston axis j, and
The angle α is 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 reciprocates. Compressor device.   2. The compressor apparatus according to claim 1, wherein the ring seal is inclined at an angle α from the reference line X in a direction opposite to a rotation direction of the crank around the rotation center h.

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