JP2000110978A - Hose joint - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hose joint to allow hose connection simply by one-step motion, with hose length adjustable properly at the side of laying the pipings, and capable of locking the fastening force at hose connection to the specified proper value. SOLUTION: A house joint is composed of an outer cylinder member 12, insert member 14 equipped with an inner cylindrical portion 32 to form a hose inserting space 34 in the area to the outer cylinder member 12, an piston 52 to partition a pressurizing space 58 upon being slidably fitted inner peripheral surface of the outer cylinder member 12, a ring-shaped fastening member 40 reducing diameterically to make deformation in association with advancing of the piston 52 under the action of the space 58 and tightening the end of each hose 10 in the radial direction, a male taper surface 50 and female taper surface 62 to give a fastening force by converting the advancing motion of the piston 52 into the diameteric contractive deformation of the ring-shaped fastening member 40, and a locking projection 68 and ring groove 20 to lock the member 40 in the tightened condition after the piston 52 has made advancing.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hose joint for connecting a hose for hydraulic piping or the like to a partner device or the like.

[0002]

2. Description of the Related Art For example, when connecting a hose for hydraulic piping to a mating device, conventionally, a metal fitting as a hose joint is caulked and fixed to an end of the hose, and the metal fitting is screwed to the mating device. Connection was made.

[0003] More specifically, as a hose fitting, an insert fitting and an outer tubular fitting (socket) each having a screw portion for screw connection with a mating device and an inner tubular portion (nipple portion) fitted into the inner peripheral surface of the end of the hose. After fitting the end of the hose into the space between the inner and outer tube fittings,
The metal fitting was fixedly attached to the end of the hose by caulking the outer metal fitting in the radial direction, and the hose was connected to the partner device via the metal fitting.

However, when the fitting is fixedly attached to the end of the hose as described above, the following inconvenience occurs. For example, when hydraulic piping is applied to a machine tool or a small construction machine, a necessary and appropriate piping length is usually determined at the stage of assembling the machine tool, the construction machine, etc., and a hose having a length corresponding to this is determined. It will be assembled to the device, but if you fix the bracket to the end of the hose in advance,
It is necessary to prepare hoses of various lengths in advance and to select and use appropriate ones from them. That is, in the related art, there is an inconvenience that extremely various kinds of hoses having various lengths must be prepared in advance.

[0005] For this reason, the length of the hose can be freely changed and adjusted at the assembly site of the hydraulic equipment such as the machine tool, that is, the construction site of the hydraulic piping, and the hose can be easily connected to the hydraulic equipment. A hose coupling has been proposed (JP-A-1-229194).

FIG. 6 shows an example. In the figure, reference numeral 200 denotes a hose as a hydraulic pipe, and reference numeral 202 denotes a hose connection portion (outer cylinder member) of a hydraulic device to be connected thereto. Reference numeral 204 denotes an insert member. The insert member 204 is located at the center of the inner space of the hose connection portion 202 and forms a hose insertion space 214 having an annular cross section on the outer peripheral side. An inner cylinder portion 206 that fits on the surface is provided.

[0008] A piston 208 is provided integrally with the inner cylinder 206 so as to be slidable on the inner peripheral surface of the hose connection 202. The pressurized space 212 communicating with the pressure fluid passage 210 is partitioned from the hose insertion space 214 so as to be separated therefrom.

Reference numeral 216 denotes a tapered member disposed inside the hose insertion space 214, and a female tapered surface 218 is provided on the inner peripheral side.
Consisting of a sleeve. This taper member 21
6 is prevented from being pulled out of the hose insertion space 214 by a retaining ring 220.

In the hose insertion space 214, an annular fastening member 222 formed of a sleeve is provided so as to be movable in the axial direction. On the outer peripheral surface of the annular fastening member 222,
A male taper surface 224 corresponding to the female taper surface 218 of the taper member 216 is formed.

In the case of this hose joint, the hose insertion space 2 is placed in the state shown in FIG. 6A, that is, with the piston and the annular fastening member 222 positioned at the left end in the figure, that is, at the retracted end.
By simply inserting the end of the hose 200 into the inside of the hose 14 and then passing the pressurized fluid through the inside of the hose 200, the hose can be easily connected.

More specifically, as shown in FIG. 1B, when a pressure fluid is passed, the pressure causes the piston 208 to move forward in the right direction in the figure, and the annular fastening member 222 is pushed out in the same direction. . Then, the annular fastening member 222 is
The diameter of the hose 200 is reduced in the radial direction by the cam action of the female tapered surface 218 of the tapered member 216 and the male tapered surface 224 of the tapered member 216, and the end of the hose 200 is clamped to a fixed state.

In the case of this hose joint, the hose can be connected without previously crimping a fitting as a joint to the end of the hose 200 as in the prior art. It has the advantage that the hose connection can be freely changed and adjusted, and the hose connection can be made extremely easily.

On the other hand, in the case of this hose joint, since the piston 208 is provided integrally with the inner cylinder 206, when the piston 208 moves forward by the action of pressure, the inner cylinder 206 is also moved by the same distance. There is a problem of moving forward.

That is, for example, assuming that the advance stroke of the piston 208 required to tighten the end of the hose 200 is 10 mm, the end of the hose 200 becomes 10 mm at the time of tightening.
It will be pushed out from the mm hose insertion space 214 to the outside.

The hose 200 is similarly connected to the other hydraulic equipment at the opposite end (not shown).
Therefore, the same amount of hose 200 is used at the opposite end.
Is pushed out. Therefore, in the case of this hose joint, the length of the hose 200 is, for example, about 20 mm longer than the appropriate pipe length in the pipe construction state.

In particular, in the case of a short pipe, the change in length of the hose 200 due to the above-mentioned extrusion is not negligible. As a result, a force for pushing the end of the hose into the hose insertion space 214 acts, and the pushing force causes the piston 208 and the annular fastening member 222 to be slightly pushed back to the left in FIG. 6, thereby weakening the fastening and fixing force to the hose end. This causes a difficult problem that the sealing performance is deteriorated.

Accordingly, the present inventors have devised a hose joint that does not cause the hose end to be pushed out when the hose is tightened, and proposed this in the earlier patent application (JP-A-10-78188).

FIG. 7 shows an example. In the figure, reference numeral 225 denotes an outer cylinder member, which is fixed to the insert member 226 by screw connection. Insert member 226
Has an inner cylindrical portion 206 and a large-diameter main body portion 228, and the main body portion 228 has a flange portion 230 and a male screw portion 2.
32 are provided.

In this hose joint, the piston 20
8 is provided separately from the inner cylinder portion 206, and the piston 208 defines a pressurized space 238 that communicates with the internal passage 210 of the inner cylinder portion 206 via the communication hole 236. The piston 208 is pushed rightward in the figure by the pressure of the fluid introduced into the pressurizing space 238, that is, is moved forward.

The piston 208 is integrally provided with a cylindrical portion 240, and a female tapered surface 218 is formed on the inner peripheral side of the cylindrical portion 240. Then, the female tapered surface 218 comes into contact with the male tapered surface 224 on the outer peripheral side of the annular tightening member 222 formed of a sleeve disposed inside the hose insertion space 214 and relatively moves in the axial direction, so that the annular tightening is performed. The diameter of the member 222 is reduced, and the hose 200 is tightened and fixed.

More specifically, in the case of the hose joint shown in FIG. 7, when the piston 208 is located at the retreating end as shown in FIG. When the piston 206 is inserted into the hose insertion space 214 to a position where it comes into contact with the stepped portion 242 of the portion 206, and a pressurized fluid such as pressure oil is passed in this state, the piston 208 and the cylindrical portion 240 integrated therewith advance rightward in the drawing. Move ((B) in the same figure)
), The annular fastening member 222 is reduced in diameter. Thus, the annular tightening member 222 tightens and fixes the end of the hose.

In the case of the hose joint shown in FIG. 7, the piston 208 is separate from the inner cylinder 206 and moves independently, and the annular fastening member 222 is fixed in position in the axial direction. Since the diameter of the hose 200 is merely reduced, the hose 200 is not pushed out of the hose insertion space 214 with the movement of the piston 208 when the end of the hose 200 is tightened and fixed. When the hose length does not change after tightening, piping can be performed with a predetermined appropriate length, and the piston 208 is pushed back in the retreating direction by the reaction force of the extrusion of the hose 200. There is no problem that the tightening force on the end of the hose is weakened and the sealing performance is reduced.

[0023]

However, in any of the hose joints shown in FIGS. 6 and 7, when a pressure such as a hydraulic pressure is applied to the piston 208, a predetermined tightening force to the hose end is maintained. However, when the action of the pressure on the piston 208 ceases, that is, when the internal pressure of the hose 200 ceases, the tightening force on the hose end may decrease due to the piston 208 returning in the retreating direction. Further, there is a problem that the hose 200 is tightened or loosened due to repeated pressurization and no pressure, thereby easily damaging the hose end.

[0024]

The hose joint of the present invention has been devised to solve such a problem.
According to the first aspect of the present invention, a hose insertion space having an annular cross section is formed between (a) the outer cylinder member and (b) the center of the inner space of the outer cylinder member and the outer cylinder member. And an insert member having an inner cylindrical portion that fits into the inner peripheral surface of the hose end in a state where the hose is inserted, and (c) slidably fits on the inner peripheral surface of the outer cylindrical member so as to fit inside the outer cylindrical member. A piston defining a pressurized space communicating with the passage of the pressurized fluid inside the inner cylindrical portion in a state in which the pressurized space is isolated from the hose insertion space; The end of the hose inserted into the hose insertion space is radially arranged by being disposed inside the space and on the outer peripheral side of the inner cylindrical portion and being reduced in diameter by the forward movement of the piston due to the action of the pressurizing space. (E) forward movement of the piston by the annular fastening member. And (f) locking the tightening mechanism in a state where the annular tightening member tightens the end of the hose after the piston is moved forward. And a lock mechanism.

According to a second aspect of the present invention, in the hose joint according to the first aspect, the annular fastening member comprises a sleeve whose diameter can be reduced in a radial direction, and the fastening mechanism includes the annular fastening mechanism. A male taper surface formed on the outer peripheral surface of the member, and a female taper that moves axially relative to the male taper surface as the piston moves forward and presses the male taper surface in the diameter reducing direction by a cam action. And a surface.

According to a third aspect of the present invention, in the hose joint according to any one of the first and second aspects, the annular fastening member comprising the sleeve is provided at a fixed position in the axial direction, and the female taper is provided. A surface is provided on a member that moves forward integrally with the piston or integrally with the piston.

According to a fourth aspect, in the hose joint according to any one of the first to third aspects, the piston is formed separately from the inner cylinder, and the piston is independent of the inner cylinder. And move forward.

According to a fifth aspect of the present invention, in the hose joint according to any one of the second to fourth aspects, the locking mechanism is configured such that, after the piston is moved forward, the male tapered surface and the female tapered surface are moved in the axial direction. It is characterized in that the relative position is fixed and the tightening force of the annular tightening member is maintained.

According to a sixth aspect of the present invention, in the hose joint according to any one of the third and fourth aspects, the locking mechanism is provided on a side of the piston having the female tapered surface or a member that moves forward integrally with the piston. And a corresponding locking claw provided on the side of the annular tightening member formed of the outer cylinder member or the sleeve, and these are locked by a forward moving end of the piston. The pawls are engaged with each other to prevent retreating movement of the piston or a member that moves forward together with the piston thereafter.

According to a seventh aspect, in the hose joint according to any one of the third and fourth aspects, the lock mechanism is provided on a side of the piston having the female tapered surface or a member that moves forward integrally with the piston. The engagement protrusion or engagement recess provided is provided on the side of the annular fastening member formed of the outer cylinder member or the sleeve, and the engagement protrusion or engagement recess is engaged with the forward moving end of the piston. In addition, it has an engaging concave portion or an engaging projection for preventing the return from being performed thereafter.

According to an eighth aspect of the present invention, in the hose joint according to the seventh aspect, the engaging projection is formed of an elastic ring whose diameter can be expanded or reduced.

According to a ninth aspect of the present invention, in the hose joint according to the seventh aspect, the engaging projection is deformed by pressing at the forward moving end of the piston and engages with the engaging recess. It is characterized by being.

[0033]

As described above, the hose joint according to the first aspect is provided with a tightening mechanism for converting the forward movement of the piston into a diameter reduction deformation of the annular tightening member and applying a tightening force. A lock mechanism that locks the tightening mechanism so that the annular tightening member maintains the tightened state is provided. According to this hose joint, even when the action of the pressure on the piston is stopped, the hose is locked to the end of the hose. Therefore, the problem of lowering the tightening force does not occur, so that the problem of deterioration of the sealing performance due to the lowering of the tightening force and the problem of damage to the hose end due to the change in the tightening force can be solved.

In the present invention, the above-mentioned annular tightening member is constituted by a sleeve, and the above-mentioned tightening mechanism is formed by a male taper surface formed on the outer peripheral surface of the annular tightening member and the piston moving forward. A female tapered surface can be configured to move relative to the male tapered surface in the axial direction and to press the male tapered surface in the diameter reducing direction by a cam action (claim 2). According to this configuration, the forward moving force of the piston can be efficiently converted into the tightening force of the annular tightening member, and the annular tightening member can be moved relative to the hose end over a predetermined range in the axial direction at the overlapping portion of the tapered surfaces. Can be applied.

Here, the annular tightening member formed of a sleeve is movable together with the piston, and a female taper surface whose position is fixed is formed on the side of the outer cylindrical member, and the annular tightening member is moved with the forward movement of the piston. While moving, the annular tightening member can be reduced in diameter by the cam action of the female taper surface and the male taper surface. In this case, the hose is inserted into the hose end by the movement of the annular tightening member. Pushing force from space works.

Here, in the hose joint according to the third aspect, an annular tightening member formed of a sleeve is provided in a fixed position in the axial direction, and a female tapered surface is provided on the member which moves forward integrally with the piston or integrally with the piston. In the case of the hose joint according to the third aspect, since the annular tightening member does not move in the axial direction when tightening the hose end portion, the pushing force of the hose due to the movement of the annular tightening member does not work. Benefits are obtained.

According to a fourth aspect of the present invention, in the hose coupling, the piston is formed separately from the inner cylindrical portion so that the piston moves forward independently of the inner cylindrical portion. When the hose end is fastened by the forward movement, there is an advantage that the hose end is not pushed out due to the forward movement of the inner cylinder.

In the present invention, the lock mechanism can fix the axial relative position between the male tapered surface and the female tapered surface after the piston moves forward (claim 5). Thus, the tightening force of the annular tightening member can be maintained, and the problem that the tightening force on the hose end is reduced when the pressure on the piston stops working can be solved. Further, it is possible to solve the problem that the end of the hose is damaged due to the repetition of the action on the piston and the release of the pressure.

According to a sixth aspect of the present invention, in the hose joint, the lock mechanism is provided with a locking claw provided on a side of a piston having a female tapered surface or a member which moves forward integrally therewith, and an outer cylinder fixed in an axial direction. 7. The hose joint according to claim 6, wherein said engaging claws are engaged with each other at a forward moving end of said piston. By stopping, it is possible to prevent the retreating movement of the piston or the member which moves forward integrally therewith. Thus, the tightening force of the annular tightening member due to the action of the male taper surface and the female taper surface can be maintained at the set tightening force. Further, in the case of the hose joint according to the sixth aspect, the lock mechanism can be simply configured, and each locking claw can be locked by utilizing the forward movement of the piston.

The locking mechanism may further comprise an engagement protrusion or an engagement recess provided on the side of the piston having the female tapered surface or the member moving forward integrally therewith, and an outer cylindrical member fixed in the axial direction. Alternatively, it may be configured to include an engagement recess or an engagement protrusion provided on the side of the annular fastening member (claim 7). Also in this case, by engaging the engagement projection or engagement recess on the moving side with the engagement advancement or engagement projection on the position fixed side at the forward movement end of the piston, the female tapered surface and the annular shape are formed. The male taper surface of the tightening member can be held in a pressing contact state, and the tightening force of the annular tightening member can be maintained at the set tightening force.

In this case, the engaging projection can be constituted by an elastic ring whose diameter can be increased or reduced. In this way, the engagement projection can be easily provided.

Alternatively, the engaging projection may be deformed by pressing at the forward moving end of the piston to engage with the engaging recess (claim 9). Also in this case, it is possible to form the engaging projection and to engage the engaging recess by effectively utilizing the forward movement of the piston.

[0043]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, embodiments of the present invention will be described in detail with reference to the drawings. In FIG. 1, reference numeral 10 denotes a resin hose;
Is an outer cylindrical member made of metal, and is fixed to the main body 16 in a state where the inner peripheral surface of one end in the axial direction is fitted water-tightly to the outer peripheral surface of the large-diameter main body 16 of the metal insert member 14. An inward flange 18 is provided at the other end of the outer cylinder member 12, and the annular groove 2 is provided inside the flange 18 following the flange 18.
0 is formed.

The main body 16 of the insert member 14 is provided with a large-diameter radially outward flange portion 22 and an annular groove 24 following the flange portion 22. An inward flange portion 30 of a metal female screw member 28 having a female screw portion 26 on the peripheral surface is rotatably fitted and assembled to the main body 16.

The insert member 14 is provided with an inner cylindrical portion 32 at the center of the inner space of the outer cylindrical member 12, and a hose insertion space 34 is provided between the inner cylindrical portion 32 and the outer cylindrical member 12. Are formed. The inner tube 32 is the hose 1
A plurality of annular protrusions 36 are formed at a predetermined pitch in the axial direction on the inner peripheral surface of the end portion of the “0” at the outer peripheral surface of the fitted portion. In addition, a passage 38 is formed in the center of the insert member 14 so as to pass therethrough in the axial direction.

Inside the hose insertion space 34, an annular fastening member 40 formed of a resin sleeve and capable of reducing the diameter is provided. The annular fastening member 40 has an outward flange portion 42 at a base end thereof.
Are fitted into the annular groove 20 of the outer cylinder member 12. The annular fastening member 40 is fixed in position in the axial direction based on the engagement between the flange portion 42 and the annular groove 20.

The annular fastening member 40 is a member for fastening the outer peripheral surface of the end of the hose 10 by reducing the diameter.
The inner peripheral surface has a plurality of annular projections 4 at a predetermined pitch in the axial direction.
4 are formed. In addition, the annular fastening member 40 includes:
As shown in detail in FIG. 2, a plurality of slits 46 and 48 for facilitating elastic deformation in the radial direction are formed alternately at predetermined intervals in the circumferential direction.

Here, the slit 46 is opened at the left end in the drawing, that is, at the end on the distal end side of the hose 10, and extends rightward in the drawing, and the other slit 48 is at the right end in the drawing, that is, at the insertion side of the hose 10. It opens at the end and extends leftward in the figure.

The annular tightening member 40 has a male tapered surface 50 formed on the outer peripheral side, and can be reduced in diameter based on a radial pressing force on the male tapered surface 50.

Reference numeral 52 denotes a piston which is separate from the inner cylindrical portion 32 of the insert member 14, and has an outer peripheral surface and an inner peripheral surface of O.
The inner peripheral surface of the outer cylindrical member 12 and the inner cylindrical portion 3 via the ring 54
2 are fitted to the outer peripheral surface of each of them so as to be watertight and slidable in the axial direction.

As shown in FIG. 1B, the piston 52 is provided with a pressurized space 58 communicating with the passage 38 through a communication hole 56 in the inner space of the outer cylinder member 12, and with the hose insertion space 34. And is formed in a blocked state, and is moved rightward in the drawing by the pressure inside the pressurized space 58. A cylindrical portion 60 is formed integrally with the piston 52, and the cylindrical portion 60 is moved forward with the piston 52 rightward in FIG.

On the inner peripheral side of the cylindrical portion 60, a female taper surface 62 having an inclination corresponding to the male taper surface 50 of the annular fastening member 40 is formed. 1, the annular tightening member 40 is reduced in diameter by the cam action of the tapered surfaces 50 and 62. That is, in this example, the male tapered surface 50 and the female tapered surface 62 convert a forward movement of the piston 52 into a diameter-reducing deformation of the annular tightening member 40 to constitute a tightening mechanism for applying a tightening force.

The cylindrical portion 60 is provided with a sharp end 64 whose thickness becomes thinner toward the front end at the shaft end (see FIG. 3A). This pointed end 64 is connected to the piston 52
As shown in FIG. 3B, the forwardly moving end of the second member is crushed to form an engagement projection 68 which engages with the inside of the annular groove 20. Here, the engagement projection 68 engages with the inside of the annular groove 20 serving as an engagement recess, and
The function is to prevent the return of the cylindrical portion 60, which is an integral part thereof, that is, the backward movement.

That is, in this example, the engagement projection 68 and the annular groove 20 as the engagement recess prevent the female tapered surface 62 integral with the piston 52 from returning to the annular fastening member 40 in the tightened state. A lock mechanism is provided to lock the lock.

Next, the operation of the hose joint of this embodiment will be described.
In the hose joint of the present example, the end of the hose 10 is inserted into the hose insertion space 34 to a position where the distal end surface thereof comes into contact with the stepped portion 66 on the outer peripheral surface of the inner cylindrical portion 32. When the pressure of the uniform fluid is applied, the piston 52 moves forward in the right direction in FIG. 1 by the pressure introduced into the pressurizing space 58, and the forward movement causes the female taper of the cylindrical portion 60 provided integrally with the piston 52. The surface 62 is the annular fastening member 4
0, and the annular fastening member 40 is reduced in diameter by the cam action of the male tapered surface 50 and the female tapered surface 62 by further forward movement. To secure the hose end.

When the piston 52 reaches the forward end, the pointed end 64 is crushed to become the engaging projection 68, which is engaged in the annular groove 20 and the cylindrical portion 60 and the piston 5
Prevent the return of 2. That is, the backward movement of the female tapered surface 62 is prevented. Here, the annular fastening member 40 is
Locked with the ends tightened.

In this embodiment, the annular groove 20 for positioning the flange 42 at the base end of the annular fastening member 40 in the axial direction is also used as the engagement recess. Alternatively, it may be formed separately on the inner peripheral surface of the outer cylinder member 12.

Further, in this example, the engaging projection 68 is formed by crushing the point 64, but the point 64 is moved outward in the radial direction by the pressing force at the forward end of the piston 52. It is also possible to bend the bent portion to form an engagement projection and engage it in the engagement recess on the outer cylinder member 12 side.

Further, an engagement recess is formed on the outer peripheral surface of the annular fastening member 40 whose axial position is fixed, and an engagement protrusion 68 provided on the cylindrical portion 60 therein and other forms of engagement. By engaging the protrusion, return of the female tapered surface 62 can be prevented.

Alternatively, an engagement recess formed on the side of the cylindrical portion 60 and an engagement projection formed on the side of the outer cylinder member 12 or the annular fastening member 40 whose position is fixed with respect to the engagement recess. It is also possible to prevent the female taper surface 62 from returning by engaging the portion.

In this case, the cylindrical portion 60 is provided integrally with the piston 52. However, the cylindrical portion 60 is provided separately from the piston 52, and the piston 52 is moved forward.
It is also possible to move the cylindrical portion 60 forward integrally.

According to the hose joint of this embodiment, the piston 52
Does not cause a problem that the tightening force on the end of the hose 10 is reduced even when the pressure applied to the hose 10 is stopped. The problem of edge damage can be solved.

Further, according to this embodiment, the forward moving force of the piston 52 can be efficiently converted into the tightening force by the annular tightening member 40, and the axial length at the overlapping portion of the male taper surface 50 and the female taper surface 62 can be increased. The tightening force by the annular tightening member 40 can be exerted on the end of the hose over a predetermined range.

In the case of the hose joint of this embodiment, the annular fastening member 4
0 does not move in the axial direction when tightening the hose end, so that there is an advantage that the pushing force of the hose 10 does not occur due to the movement of the annular tightening member 40, and similarly, when the hose end is tightened, There is an advantage that the pushing force of the hose end caused by the forward movement of the tubular portion 32 is not generated.

In addition, in this embodiment, the locking force of the annular tightening member 40 can be held by the lock mechanism, and the tightening force on the hose end can be reduced even when the pressure on the piston 52 is no longer applied. Does not cause any degradation problems. Further, there is no problem that the end of the hose is damaged due to the repetition of the action of the pressure on the piston 52 and the release of the pressure.

In the case of the hose joint of this embodiment, the annular fastening member 4
0 is fixed in the axial direction.
It also has the advantage that the workability of inserting 0 is good. That is,
If the annular tightening member 40 moves in the axial direction when the hose 10 is inserted, the male tapered surface 50 and the female tapered surface 62
The diameter of the annular tightening member 40 is reduced by the action of the above, which causes the inconvenience that the hose 10 is tightened in a state where it is not fully inserted, and the insertion becomes difficult.
In this example, since the position of the annular fastening member 40 is fixed, such an inconvenience does not occur, and the end of the hose 10 can be smoothly inserted.

When the end of the hose 10 is fastened by the annular fastening member 40 having the slits 46 and 48, as shown in FIG.
The cover layer 70 protrudes into the slits 46 and 48 due to the locally large tightening force of the annular protrusion 44 of the annular tightening member 40 with respect to 0, and as a result, the entire thickness of the cover layer 70 becomes thin and early. There is a problem that the cover layer 70 breaks and eventually the hose 10 breaks.

In particular, a large local stress concentration occurs in the cover layer 70 at the annular protrusion 44 at the right end position in the figure, and there is a problem that a protrusion 76 is formed in the vicinity of the cover layer 70 into the inside of the slit 46 (FIG. 3C). (B)). Reference numeral 78 denotes a protruding portion to the other slit 48, and the protruding portion 78 is not as large as the protruding portion 76 to the slit 46.

FIG. 3C shows a form of an annular tightening member 40A as a comparative example, in which one slit 46A is provided with the most local annular tightening force at the right end in the figure. It extends to the position of the part 44.

When the slit 46A extends to the position of the right end annular protrusion 44, the cover layer 70 has a large protrusion 76 into the slit 46A near the right end of the annular protrusion 44, as a result. In addition, the thickness of the cover layer 70 is reduced.

FIG. 7B shows the form of the sleeve 40 of the present example configured to solve this problem in detail.
As shown in the figure, here, one slit 46 does not reach the position of the annular protrusion 44 at the right end in the figure, but extends only to the position immediately before it.

For this reason, the sectional views (B) and (B) of the hose 10 at the respective positions S of the annular fastening members 40 and 40A are
(C) As is clear from the comparison with (b), the annular fastening member 4
At 0, the large protruding portion 76 as in the annular fastening member 40A is not formed, and the thickness of the cover layer 70 is increased by that amount, so that the dynamic pressure durability life of the hose 10 is extended. . In addition, FIG.
Reference numerals 72 and 74 denote tubes as a reinforcing layer and an inner surface layer of the hose 10.

By the way, when a dynamic pressure test was performed using the hose 10 having the following configuration under the following conditions, when the annular fastening member 40A having the configuration shown in FIG. The dynamic tightening member 4 shown in FIG.
When 0 was used, no breakage of the cover layer 70 was observed even when the number of dynamic pressure repetitions reached one million. Note that these are the results of a test performed on six hoses.

1. Hose configuration <Tube 74> Material: Polyester elastomer (made by Toray Dupont)
Hytrel 5577) One thickness: 0.9mm Inner diameter: φ9.5mm <Reinforcing layer 72> Material: Polyester thread (Toray Tetoron TF702)
C, 35T / m) 1500D / 2 <Cover layer 70> Material: Polyurethane (PANDIC T- made by DIC)
8195 BLACK) One thickness: 0.45mm

2. Test method 0⇔140 kgf / cm according to JIS-B-8362A
The dynamic pressure (oil pressure) of No. ² was repeatedly applied, and the number of repetitions leading to cover breakage was determined. The oil temperature was 100 ° C.

FIG. 4 shows another embodiment of the lock mechanism. In this embodiment, the outer peripheral surface of the annular fastening member 40 and the cylindrical portion 6 are formed.
Locking claws 80 and 82 are provided on the inner peripheral surface of the piston 0, respectively, and the locking claws 80 and 82 are locked to each other at the forward end of the piston 52, thereby preventing the female taper surface 62 from returning. Thus, the annular tightening member 40 is locked in the tightened state.

Even in such a case, the annular fastening member 40 can be locked in a state where the end of the hose 10 is fastened, and the same effects as in the embodiment of FIGS. be able to. Also in this example, the lock mechanism can be easily configured, and the annular tightening member 40 can be easily locked in the tightened state using the forward movement of the piston 52.

In this embodiment, one locking claw 80 is provided on the inner peripheral side of the fixed outer cylinder member 12 and the other locking claw 82 is provided on the outer peripheral side of the cylindrical portion 60.
By locking them together at the two advanced ends, the return of the female tapered surface 62 can be prevented.

FIG. 5 shows still another embodiment of the lock mechanism. In this example, an annular groove 86 is formed on the outer peripheral surface of the cylindrical portion 60, and an elastic C-ring 88 is attached thereto in a reduced diameter state.
The elastic C-ring 88 is expanded and deformed in diameter, and a part of the elastic C-ring 88 is elastically fitted into an annular groove 90 formed at a corresponding position on the inner peripheral surface of the outer cylinder member 12. The annular groove 86 on the outer peripheral surface and the annular groove 90 on the inner peripheral surface of the outer cylinder member 12 are positioned so as to straddle, thereby preventing the female taper surface 62 from returning.

Here, the elastic C-ring 88 forms an engagement projection, and the annular groove 90 forms an engagement recess. These constitute a lock mechanism for locking the annular fastening member 40 in the tightened state.

Also in this embodiment, since the annular tightening member 40 can be locked in the tightened state at the forward end of the piston 52, the same effect as that of the embodiment shown in FIGS. 1 to 3 can be obtained.

That is, the end of the hose 10 can be held in a tightly clamped state even when the pressure action on the piston 52 is stopped. The problem that the hose end is damaged by the decrease in the tightening force on the end of the hose 10 to cause a seal leak or the increase and decrease of the tightening force on the hose end due to the repetition of the action of the pressure and the release thereof. Can be solved.

Also in this embodiment, the lock mechanism can be simply constructed, and the annular tightening member 40 can be easily locked in the tightened state by using the forward movement of the piston 52.

The embodiments of the present invention have been described above in detail, but these are merely examples. For example, in the above-described embodiment, the female screw member 28 is attached to the insert member 14, and the hose 10 is connected to the other device via the female screw member 28. However, the hose 10 shown in FIG. By configuring the device main body as an outer cylindrical member, the hose 10 can be directly connected to the device of the other party, and also, as in the hose joint shown in FIG.
In some cases, the piston may be provided integrally with the inner cylinder and the inner cylinder and the piston may be moved forward so that the end of the hose is fastened and fixed by the annular fastening member. Further, the present invention can be configured in a form in which various changes are made without departing from the gist thereof, such as being applicable as a rubber hose joint.

[Brief description of the drawings]

FIG. 1 is a view showing a hose joint according to an embodiment of the present invention.

FIG. 2 is an exploded view showing the hose joint in FIG. 1 into components.

FIG. 3 is an explanatory diagram showing a main part of the embodiment together with its advantages.

FIG. 4 is a view showing an example of a form different from FIG. 1 of the lock mechanism according to the present invention.

FIG. 5 is a view showing an embodiment of a lock mechanism according to the present invention which is different from FIGS. 1 and 4;

FIG. 6 is a view showing an example of a conventional hose joint.

FIG. 7 is a view showing an example of a conventional hose joint different from FIG. 6;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Hose 12 Outer cylinder member 14 Insert member 20 Annular groove (engagement concave part) 32 Inner cylinder part 34 Hose insertion space 38 Passage 40 Annular fastening member 50 Male taper surface 52 Piston 56 Communication hole 58 Pressurized space 60 Cylindrical part 62 Female Tapered surface 64 Pointed end 68 Engagement projection 80, 82 Locking claw 88 Elastic C-ring (engagement projection) 90 Engagement groove (engagement recess)

Claims (9)

[Claims] 1. A hose insertion space having an annular cross section is formed between (a) an outer cylinder member and (b) a center portion of an inner space of the outer cylinder member and the outer cylinder member. And an insert member having an inner cylindrical portion fitted into the inner peripheral surface of the hose end portion, and (c) the inner cylindrical portion inside the outer cylindrical member slidably fitted to the inner peripheral surface of the outer cylindrical member. And (d) a radially-reducible member which is formed in a state in which a pressurized space communicating with a passage of the pressurized fluid inside the hose is separated from the hose insertion space. An annular fastener that is disposed on the outer peripheral side of the cylindrical portion and is reduced in diameter as the piston moves forward due to the action of the pressurizing space, and radially tightens the end of the hose inserted into the hose insertion space. And (e) changing the forward movement of the piston into a reduced diameter deformation of the annular fastening member. And a lock mechanism for applying a tightening force and (f) a lock mechanism for locking the tightening mechanism in a state where the annular tightening member tightens the end of the hose after the piston moves forward. A hose joint characterized by having. 2. The hose coupling according to claim 1, wherein
The annular tightening member is formed of a sleeve whose diameter can be reduced in the radial direction, and the tightening mechanism includes a male taper surface formed on an outer peripheral surface of the annular tightening member, and a forward movement of the piston. And a female tapered surface which moves relative to the male tapered surface in the axial direction and presses the male tapered surface in the radial direction by a cam action. 3. The hose coupling according to claim 1, wherein the annular fastening member made of the sleeve is provided at a fixed position in the axial direction, and the female tapered surface is attached to the piston. A hose joint provided on a member that moves forward integrally or integrally with the piston. 4. The hose coupling according to claim 1, wherein the piston is separate from the inner cylinder, and the piston moves forward independently of the inner cylinder. A hose joint characterized by the above. 5. The hose joint according to claim 2, wherein the lock mechanism fixes an axial relative position between the male tapered surface and the female tapered surface after the piston moves forward. A hose joint characterized in that it retains the tightening force of the annular tightening member. 6. The hose coupling according to claim 3, wherein the lock mechanism is provided on a side of the piston having the female tapered surface or a member that moves forward integrally with the piston. A locking claw and a corresponding locking claw provided on the side of the annular fastening member formed of the outer cylinder member or the sleeve, and locking the locking claws to each other at a forward moving end of the piston. A hose joint characterized in that it prevents the piston or a member that moves forward together with the piston from moving backward. 7. The hose coupling according to claim 3, wherein the locking mechanism is provided on a side of the piston having the female tapered surface or a member that moves forward with the piston. A protrusion or engagement recess, provided on the side of the annular tightening member formed of the outer cylinder member or the sleeve, and engaged with the engagement protrusion or engagement recess at the forward moving end of the piston, and A hose joint having an engagement recess or an engagement protrusion for preventing return. 8. The hose coupling according to claim 7, wherein
The hose joint, wherein the engagement projection is formed of an elastic ring whose diameter can be increased or decreased. 9. The hose coupling according to claim 7, wherein
The hose joint, wherein the engagement protrusion is deformed by pressing at a forward movement end of the piston to engage the engagement recess.