JP2014083830A - Puncture repair kit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a puncture repair kit in which the feed pressure of compressed air to a tire and a bottle unit is regulated to a prescribed pressure or below while eliminating a relief valve, or the back flow of a puncture repair liquid to the side of a compressor apparatus of a puncture repair liquid is prevented.SOLUTION: The puncture repair kit comprises: a compressor apparatus under the prescribed pressure Pprovided with no relief valves; and a bottle unit. In the compressor apparatus, provided that cylinder volume (stroke volume) in a meanwhile in which a piston moves from the bottom dead center to the top dead center is defined as V1, the cylinder volume (compression volume) when the piston reaches the bottom dead center is defined as V2, the atmospheric pressure is defined as Pand the prescribed pressure is defined as P, the compression volume V2 satisfies the following formula (1). In a suction valve provided in the piston, the diameter D of the suction hole is controlled to 3 to 15 mm:0.8×{V1×P/(P-P)≤V2<1.0×{V1×P/(P-P)}(1) The bottle unit is not disposed with one way valves for preventing the back flow of a puncture repair liquid to the side of the compressor apparatus.

Description

  The present invention relates to a tire puncture repair kit for repairing a puncture emergency by sequentially injecting a puncture repair liquid and compressed air into a punctured tire.

  As a puncture repair kit for repairing a puncture as soon as possible, a kit shown in FIG. 9A has been proposed (see, for example, Patent Document 1). This puncture repair kit includes a compressor device a that generates compressed air, and a bottle unit b in which a cap b2 is attached to the mouth of a bottle container b1 that contains a puncture repair liquid.

  The cap b2, as conceptually shown in FIG. 9B, has an air intake port d1 for sending compressed air from the compressor device a into the bottle container b1 through the first flow path c1; The compressed air is provided with a take-out port d2 for sequentially taking out the puncture repair liquid and compressed air from the bottle container b1 through the second flow path c2 to the tire T side.

  The compressor device a has a cylinder f for accommodating the piston e so as to be capable of reciprocating. The cylinder f forms a pump chamber f1 that compresses air with the piston e, and a surge chamber f2 that receives the compressed air compressed in the pump chamber f1 through an exhaust valve (not shown). Yes. The surge chamber f2 is connected with a relief valve g for releasing the overpressure when the supply pressure of the compressed air exceeds a specified pressure. The specified pressure is normally set to the allowable maximum pressure of the tire, and the tire is prevented from being damaged by filling with a pressure exceeding the specified pressure.

  On the other hand, as shown in FIG. 10, the relief valve g includes a cylindrical valve case i whose front end portion is attached to the surge chamber f2 of the cylinder f, and the front end of the valve case i has an air inlet h1. Is formed (see, for example, Patent Document 2). In the center hole h, a valve body k that opens and closes the air inlet h1 and a coil spring n that biases the valve body k toward the air inlet h1 are disposed, and the center hole h An adjustment cap j having an exhaust hole j1 and screwed back and forth is attached to the end. When assembling the relief valve g, the adjustment cap j is screwed back and forth to adjust the urging force of the coil spring n so that the relief valve g operates at the specified pressure (relief pressure).

  As described above, the relief valve g has a large number of parts, and the adjustment work is required for all the relief valves when assembled. For this reason, a lot of time and labor are required for production, which is one of the causes of productivity reduction and cost increase in the compressor apparatus.

  In addition, when the puncture repair liquid is injected into the tire T using the compressor device a, the pressure in the bottle container b1 gradually increases in the abnormal operation state such as the tire valve portion being clogged in the middle, and the specified pressure When (relief pressure) is exceeded, the relief valve g is actuated to release the overpressure. However, since the pressure drop occurs when the compressed air is released from the relief valve g, the puncture repair liquid in the bottle container b1 flows back to the surge chamber f2 side and is released together with the overpressure air from the relief valve g. There is.

  In particular, in the puncture repair kit in which the compressor device a and the compressor device a are directly connected, the flow path from the bottle container b1 to the surge chamber f2 is short, and thus the problem of the backflow becomes greater. Therefore, conventionally, as shown in Patent Document 1, a one-way valve r for preventing the backflow is formed in the first flow path c1.

  However, the one-way valve r is one of the causes of cost increase because of the large number of parts, like the relief valve g.

JP 2010-249010 A JP 2012-101450 A

  Therefore, the present invention can regulate the supply pressure of the compressed air to the tire or bottle unit to a specified pressure or less while eliminating the relief valve, and suppress damage due to overpressure of the tire or bottle unit. The purpose of the present invention is to provide a puncture repair kit that can prevent backflow of puncture repair liquid to the compressor device side while eliminating one-way valve, and can improve productivity and reduce costs. Yes.

In order to solve the above-mentioned problems, the invention of claim 1 of the present application relates to a compressor device in which the supply pressure of compressed air is regulated to a specified pressure _PP or less without providing a relief valve, and a bottle container opening containing puncture repair liquid. A puncture repair kit comprising a bottle unit with a cap attached to the part,
The cap includes an air intake port through which compressed air from the compressor device is fed into the bottle container through the first flow path, and puncture repair liquid and compressed air from the bottle container by feeding the compressed air. With a take-out port for sequentially taking out the two channels,
Moreover, the first flow path is not provided with a one-way valve that prevents the puncture repair liquid from flowing backward to the compressor device side,
The compressor device is
motor,
A piston driven by the motor via a crank mechanism;
A cylinder main body that forms a pump chamber that compresses air between the piston and reciprocally moves from bottom dead center to top dead center, and an exhaust valve that compresses compressed air compressed in the pump chamber. A cylinder having a cylinder sub-portion forming a surge chamber received via
An intake valve having an intake hole that penetrates the piston and sucks outside air into the pump chamber, and a valve body that is a plate spring that elastically closes the intake hole from the pump chamber side;
And an air supply passage for supplying compressed air from the surge chamber to the bottle unit side,
Moreover, the stroke volume that is the cylinder volume while the piston moves from the bottom dead center to the top dead center is V1, the compression volume that is the cylinder volume when the piston reaches the top dead center is V2, and the atmospheric pressure is P _{When 0} , the compression volume V2 satisfies the following formula (1), and
The diameter D of the intake hole is 3 to 15 mm.
_{0.8 × {V1 × P 0 /} (P P -P 0)} ≦ V2 <1.0 × {V1 × P 0 / (P P -P 0)} --- (1)

  According to a second aspect of the present invention, the valve body has a thickness t of 0.05 to 0.2 mm.

  According to a third aspect of the present invention, the air intake port portion of the cap is directly connected to the compressor device.

The pressures P _P and P ₀ are absolute pressures.

  In the present invention, as described above, the compression volume V2 of the cylinder of the compressor device is set so as to satisfy the formula (1).

Here, from Boyle's law, the product of the air pressure and volume {P ₀ × (V1 + V2)} in the state where air is sucked into the cylinder at the bottom dead center is compressed to the maximum pressure Pmax at the top dead center. It coincides with the product (Pmax × V2) of the pressure and volume of air in the cylinder in the above state. That is, the relationship of the following formula (a) is obtained. From the above formula (A), the compression volume V2 is obtained as shown in the formula (A).
_{Pmax × V2 = P 0 × (} V1 + V2) --- ( a)
_{V2 = (P 0 × V1)} / (Pmax -P 0) --- ( a)

  On the other hand, when the air pressure in the surge chamber gradually increases and becomes equal to the maximum pressure Pmax, the pressure inside and outside the exhaust valve is balanced. Therefore, the compressed air in the cylinder is not discharged to the surge chamber side and stays in the cylinder. That is, in spite of the operation of the piston, neither the intake nor the exhaust into the cylinder is performed, and the supply pressure from the compressor device does not rise above the maximum pressure Pmax in the cylinder.

Therefore, by setting the specified pressure P _P of the compressor device as the maximum pressure Pmax, the supply pressure from the compressor device can be restricted to the specified pressure P _P or less without using a relief valve, and the compression volume V2 for that can be reduced. The following equation (c) can be obtained.
_{V2 = (P 0 × V1)} / (P P -P 0) --- ( c)

However, in reality, there is a tendency that the air intake amount at the bottom dead center is insufficient due to the influence of the intake valve, and therefore the actual compression volume V2 is (P ₀ × V1) / (P _P −P ₀ ). It is necessary to set smaller than this. However, if the compression volume V2 is too small, there arises a new problem that the exhaust efficiency is lowered due to a time delay in the opening and closing of the intake valve. Therefore, in the present invention, the compression volume V2 is set to 0.8 of (P ₀ × V1) / (P _P −P ₀ ) by restricting the diameter of the intake hole and reducing the intake resistance in the intake valve as much as possible. While ensuring more than twice, this suppresses a decrease in exhaust efficiency.

  In the compressor device, since the relief valve is eliminated, the bottle container and the surge chamber are both at the specified pressure and the same pressure even in an abnormal operation state such as a tire valve portion being clogged. Therefore, the back flow of the puncture repair liquid to the surge chamber side does not occur, and the one-way valve of the first flow path can be eliminated.

It is a perspective view which shows an example of the use condition of the puncture repair kit of this invention. It is sectional drawing which shows one Example of a compressor apparatus. It is a perspective view which shows the principal part of a compressor main body. It is sectional drawing which shows the principal part of a compressor main body. It is a disassembled perspective view which shows an intake valve. It is a schematic sectional drawing explaining the stroke volume V1 and the compression volume V2. It is sectional drawing which shows a cap with a bottle container. It is a fragmentary sectional view which shows the connection state of a compressor apparatus and a bottle unit. (A) is a perspective view which shows the conventional puncture repair kit, (B) is sectional drawing which shows the internal structure notionally. It is sectional drawing which shows the relief valve used for a compressor apparatus.

Hereinafter, embodiments of the present invention will be described in detail.
As shown in FIG. 1, the puncture repair kit 1 of the present embodiment includes a compressor device 2 that regulates the supply pressure of compressed air to a specified pressure _PP or less without providing a relief valve, and compressed air from the compressor device 2. And a bottle unit 3 operated by

  As shown in FIG. 2, the compressor device 2 accommodates a compressor body 4 that generates compressed air in a storage case 9 so as to be integrally transportable. The compressor body 4 includes a motor M, a piston 5 coupled to the motor M via a crank mechanism 11, a cylinder 7 that accommodates the piston 5 in a reciprocating manner, and an intake valve 12 ( 3 to 5) and an air supply passage 8 (shown in FIGS. 3 and 4) for supplying the generated compressed air to the bottle unit 3 side.

  The storage case 9 forms a flat, substantially rectangular parallelepiped box having a small height. 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 provided with a power plug 10 that can be connected to a cigarette lighter socket of an automobile is connected to the motor M via a power switch SW that is attached to the upper plate portion of the storage case 9. As the crank mechanism 11, various known structures can be employed.

  The cylinder 7 includes a cylinder body 7A and a cylinder sub-portion 7B as shown in FIGS. The cylinder body 7A accommodates the piston 5 in a reciprocating manner from a bottom dead center PL (shown in FIG. 6) to a top dead center PU, and a pump chamber 6A for compressing air between the piston 5 and the cylinder 5A. Form. The cylinder sub-portion 7B is connected to the cylinder body 7A, and forms a surge chamber 6B that receives the compressed air compressed in the pump chamber 6A through the exhaust valve 13. The surge chamber 6B suppresses the pulsation of compressed air from the pump chamber 6A and stabilizes the pressure. The cylinder sub-portion 7B is formed with connecting portions 15 and 16. One connecting portion 15 is connected to a pressure gauge 17 for measuring the pressure in the surge chamber 6B. The other connecting portion 16 is formed with the air supply flow path 8, and the tip of the connecting portion 16 is directly connected to the bottle unit 3.

  The exhaust valve 13 includes a conduction hole 13A for conducting the pump chamber 6A and the surge chamber 6B, a valve body 13B for closing the conduction hole 13A from the surge chamber 6B side, such as a rubber member, and the valve body 13B. Coil spring-like spring means 13C arranged between the cylinder sub-part 7B and the lid part 7B1 and biasing the valve body 13B toward the conduction hole 13A. The exhaust valve 13 is activated by pressurization of the pump chamber 6A, and opens the conduction hole 13A. The operating force at this time is preferably as small as possible, 80 kPa or less, and further 50 kPa or less when converted to the pressure to the valve body 13B.

  The intake valve 12 includes an intake hole 12A that passes through the piston 5 and sucks outside air into the pump chamber 6A, and a valve body 12B that elastically closes the intake hole 12A from the pump chamber 6A side. . Specifically, as shown in FIG. 5, the valve body 12B is made of a metal leaf spring. In this example, the fixed portion 12B1 is fixed to the upper surface of the piston 5 by using, for example, a screw fitting 14 or the like. And a substantially disc-shaped covering portion 12B2 that covers the intake hole 12A, and a constricted portion 12B3 disposed therebetween. The constricted portion 12B3 facilitates elastic deformation, and when descending from the top dead center PU, the intake hole 12A is opened by the negative pressure in the pump chamber 6A, and outside air is sucked into the pump chamber 6A. Further, when rising from the bottom dead center PL, the intake hole 12A can be closed by the elasticity of the valve body 12B and the pressurization in the pump chamber 6A.

In the present invention, in order to restrict the supply pressure of the compressed air from the compressor device 2 to a specified pressure _PP or less without providing a relief valve, the compression volume V2 of the cylinder 7 is larger than the conventional one, and The range shown in (1) is set.

Specifically, as shown in FIG. 6, the stroke volume, which is the cylinder volume while the piston 5 moves from the bottom dead center PL to the top dead center PU, is V1, and when the piston 5 reaches the top dead center PU. the compression volume is the cylinder volume V2, when the atmospheric pressure was set to P _0, the compression volume V2, is set in a range satisfying the following equation (1).
_{0.8 × {V1 × P 0 /} (P P -P 0)} ≦ V2 <1.0 × {V1 × P 0 / (P P -P 0)} --- (1)

Here, from Boyle's law, the product of air pressure and volume {P ₀ × (V1 + V2)} in the cylinder 7 in a state where air is sucked into the cylinder 7 at the bottom dead center PL is the maximum pressure at the top dead center PU. This corresponds to the product (Pmax × V2) of the pressure and volume of air in the cylinder 7 in a state compressed to Pmax. That is, the relationship of the following formula (a) is obtained. From the above formula (A), the compression volume V2 is represented by the formula (A).
_{Pmax × V2 = P 0 × (} V1 + V2) --- ( a)
_{V2 = (P 0 × V1)} / (Pmax -P 0) --- ( a)

  On the other hand, when the air pressure in the surge chamber 6B gradually increases and becomes equal to the maximum pressure Pmax, the pressure inside and outside the exhaust valve 13 is balanced. Therefore, the compressed air in the cylinder 7 is not discharged to the surge chamber 6B side and remains in the cylinder 7. That is, although the piston 5 is operated, neither intake nor exhaust into the cylinder 7 is performed, and the supply pressure from the compressor device 2 does not rise above the maximum pressure Pmax.

Accordingly, the maximum pressure Pmax as by setting a specified pressure P _P of the compressor unit 2, without using a relief valve can regulate the supply pressure from the compressor unit 2 to the specified pressure P _P below, the compression volume for the Theoretically V2 is obtained by the following equation (c).
_{V2 = (P 0 × V1)} / (P P -P 0) --- ( c)

Note for puncture repair of a tire, or in the case of a compressor device for pumping a tire, as the specified pressure P _P, it is preferable to employ a permissible maximum pressure of the tire, for example, in the case of passenger car tires, 451.3KPa (gauge The pressure is preferably 350 kPa in terms of pressure, 701.3 kPa (600 kPa in terms of gauge pressure) in the case of light truck tires, and 901.3 kPa (800 kPa in terms of gauge pressure) in the case of heavy load tires.

However, in reality, due to the influence of the intake valve 12, there is a tendency that the amount of air sucked at the bottom dead center PL is insufficient. Therefore, the actual compression volume V2 needs to be set smaller than the value (P ₀ × V1) / (P _P −P ₀ ). However, if the compression volume V2 is too small, there is a new problem that a time delay occurs in the opening and closing of the intake valve 12 and the exhaust efficiency of the compressor is significantly reduced.

Therefore, in the present invention, the compression volume V2 is set to the value (P ₀ × V1) / (P by regulating the diameter D (shown in FIG. 5) of the intake hole 12A and suppressing the intake resistance in the intake valve 12. _While ensuring 0.8 times or more of ( _P− P ₀ ), this suppresses a decrease in exhaust efficiency.

  Specifically, the diameter D of the intake hole 12A is restricted to a range of 3 to 15 mm. When the diameter D is less than 3 mm, the amount of intake air is insufficient, and the exhaust efficiency of the compressor is reduced. On the other hand, when the diameter D exceeds 15 mm, the valve body 12B is made of a thin leaf spring, so that the airtightness to the intake hole 12A becomes insufficient and the exhaust efficiency is lowered. Therefore, the lower limit of the diameter D is preferably 5 mm or more, and the upper limit is preferably 10 mm or less.

  At this time, the thickness t (shown in FIG. 5) of the valve body 12B is preferably 0.05 to 0.2 mm. If the thickness t exceeds 0.2 mm, the inertial resistance during piston operation increases. The bending rigidity of the valve body 12B becomes excessive, and the intake hole 12A is not sufficiently opened, leading to a shortage of intake air. On the other hand, when the thickness t is less than 0.05 mm, the rigidity of the valve body 12B is insufficient and the airtightness to the intake hole 12A becomes insufficient, leading to a decrease in exhaust efficiency. From such a viewpoint, the lower limit of the thickness t is more preferably 0.07 mm or more, and the upper limit is more preferably 0.15 mm or less. From the same viewpoint, the width W (shown in FIG. 5) of the constricted portion 12B3 is preferably set to 10 mm or less in order to suppress the intake amount deficiency.

In addition, as the said valve body 12B, the stainless steel material excellent in especially corrosion resistance can be employ | adopted suitably.
The covering portion 12B2 is preferably formed with a diameter that is 1 to 5 mm larger than the diameter D of the intake hole 12A.

  Next, as shown in FIG. 1, the bottle unit 3 includes a bottle container 18 containing a puncture repair liquid, and a cap 19 attached to the mouth portion.

  As shown in FIG. 7, the bottle container 18 protrudes from the lower end of the body portion 18B with a small-diameter cylindrical mouth portion 18A through which puncture repair liquid can be taken in and out.

  The cap 19 can be directly connected to the discharge port portion 16A at the tip of the connecting portion 16 of the compressor device 2, and an intake port portion 41 for sending compressed air from the discharge port portion 16A into the bottle container 18; Is provided with an outlet 42 for sequentially taking out the puncture repair liquid and compressed air from the bottle container 18.

  Specifically, the cap 19 is a cap body integrally including a bottom plate portion 31 forming a bottom surface, a bottle mounting portion 32 to which the mouth portion 18A of the bottle container 18 is attached, and a constricted portion 33 disposed therebetween. 19A. Further, in the cap main body 19A, a first flow path 35 extending from the intake port portion 41 into the mouth portion 18A of the bottle container 18 and a discharge port portion 42 extending into the mouth portion 18A of the bottle container 18 are provided. A second flow path 36 is formed.

  The bottle attachment portion 32 has an attachment recess 32A for fixing the mouth portion 18A, and a boss portion 32B protruding from the bottom surface of the attachment recess 32A. The mounting recess 32A can be screwed into the mouth portion 18A with an internal screw provided on the inner wall surface thereof. On the upper surface of the boss portion 32B, a first flow path opening 35a that forms the upper end of the first flow path 35 and a second flow path opening 36a that forms the upper end of the second flow path 36 are provided. Each is open.

  Further, in this example, the intake port portion 41 is a connection nozzle protruding from the constricted portion 33 toward the discharge port portion 16A. As shown in FIG. 8, the connection nozzle (intake port portion 41) is a connection nozzle. By fitting in the discharge port portion 16A, direct connection is made without using a hose.

  In the puncture repair kit 1 of this example, a fixing means 34 is provided to prevent the discharge port portion 16A and the intake port portion 41 from being disconnected and the puncture repair liquid from contaminating the surrounding area during puncture repair. It is done.

  The fixing means 34 includes a locking means 34A formed on the cap 19 and a retaining means 34B formed on the compressor device 2. In this example, the locking means 34A protrudes toward the compressor device 2 on both sides (upper and lower in this example) of the intake port 41 and has a pair of locking hooks provided with a right-angled triangular hook at the tip. It consists of nails 45. Further, in this example, the retaining means 34B is provided at a position facing the locking claw 45 and has a claw engagement hole 46 that can be engaged with the locking claw 45 and can be prevented from coming off.

In such a puncture repair kit 1, the compressor device 2 does not include a relief valve. Therefore, even if the abnormal operation state such as a tire valve portion in the puncture repair liquid injected clogging occurs, the inside and the surge chamber 6B bottle 18, no Toko both greater than specified pressure P _P, moreover The pressure is the same. Therefore, there is no occurrence of backflow of the puncture repair liquid from the bottle container 18 to the surge chamber 6B. Therefore, the one-way valve for preventing the back flow of the puncture repair liquid is not provided in the first flow path 35 of the bottle unit 3.

  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)
In order to confirm the effect of the present invention, the compressor device shown in FIG. Each compressor device was connected to a tire, and the maximum pressure P when the compressor device was left in an operating state was measured using a pressure gauge 17 attached to the cylinder sub-portion 7B. For comparison, a similar test was performed on a conventional compressor device (conventional example) having a relief valve with a relief pressure set to 451.3 kPa (350 kPa in terms of gauge pressure). The pressure P was measured.

  Except as described in the table, the specifications are substantially the same, and each compressor device uses a metal (stainless steel) leaf spring having a generally bowl shape (neck width 7 mm) as the valve body 12B of the intake valve 12. Yes. The operating force of the exhaust valve 13 (converted to the pressure on the valve body) is 30 kPa.

Exhaust efficiency:
The exhaust efficiency was compared with the ratio To / T × 100 (%) where To is the time of the conventional example when the voltage is 12 V, the tire pressure is increased to 250 kPa (gauge pressure), and T is the time of the example. The larger the value, the better the exhaust efficiency.

  As shown in the table, the compressor device of the embodiment can regulate the supply pressure of the compressed air to the tire (filled air) at a substantially specified pressure without providing a leaf valve and maintaining high exhaust efficiency. Can be confirmed.

(2)
7 is connected to the conventional compressor unit shown in Table 1 (one valve is not provided in the first flow path), and the puncture repair kit is activated with the tire valve part clogged. Let it go. As a result, it was confirmed that the puncture repair liquid was discharged from the relief valve together with the compressed air when the relief valve was operated in the untreated state.

  On the other hand, the bottle unit having the structure shown in FIG. 7 (not provided with a one-way valve in the first flow path) is connected to the compressor device of Example 1 shown in Table 1, and the tire valve portion is similarly clogged. In this state, the puncture repair kit was operated and left. As a result, no leakage of the puncture repair liquid was observed in the standing state.

DESCRIPTION OF SYMBOLS 1 Puncture repair kit 2 Compressor apparatus 3 Bottle unit 5 Piston 6A Pump chamber 6B Surge chamber 7 Cylinder 7A Cylinder main body 7B Cylinder sub-portion 8 Air supply flow path 11 Crank mechanism 12A Intake hole 12B Valve body 12 Intake valve 13 Exhaust valve 18 Bottle Container 18A Mouth 19 Cap 35 First channel 36 Second channel 41 Intake port 42 Extraction port M Motor,
PL bottom dead center PU top dead center

Claims (3)

In puncture repair kit comprising a compressor device which regulates the supply pressure of the compressed air below a specified pressure P _P without providing a relief valve, and a bottle unit fitted with a cap to the mouth portion of the bottle container containing a puncture repair liquid There,
The cap includes an air intake port through which compressed air from the compressor device is fed into the bottle container through the first flow path, and puncture repair liquid and compressed air from the bottle container by feeding the compressed air. With a take-out port for sequentially taking out the two channels,
Moreover, the first flow path is not provided with a one-way valve that prevents the puncture repair liquid from flowing backward to the compressor device side,
The compressor device is
motor,
A piston driven by the motor via a crank mechanism;
A cylinder main body that forms a pump chamber that compresses air between the piston and reciprocally moves from bottom dead center to top dead center, and an exhaust valve that compresses compressed air compressed in the pump chamber. A cylinder having a cylinder sub-portion forming a surge chamber received via
An intake valve having an intake hole that penetrates the piston and sucks outside air into the pump chamber, and a valve body that is a plate spring that elastically closes the intake hole from the pump chamber side;
And an air supply passage for supplying compressed air from the surge chamber to the bottle unit side,
Moreover, the stroke volume that is the cylinder volume while the piston moves from the bottom dead center to the top dead center is V1, the compression volume that is the cylinder volume when the piston reaches the top dead center is V2, and the atmospheric pressure is P _{When 0} , the compression volume V2 satisfies the following formula (1), and
A puncture repair kit characterized in that the diameter D of the intake hole is 3 to 15 mm.
_{0.8 × {V1 × P 0 /} (P P -P 0)} ≦ V2 <1.0 × {V1 × P 0 / (P P -P 0)} --- (1)   The puncture repair kit according to claim 1, wherein the valve body has a thickness t of 0.05 to 0.2 mm.   The puncture repair kit according to claim 1, wherein the air intake port portion of the cap is directly connected to the compressor device.

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