JPS58102608A - Rotary fluid hydraulic cylinder for chucking in machine tool - Google Patents

Abstract

PURPOSE:To improve the performance of a rotary oil hydraulic cylinder by cooling the surface of the rotary cylinder with the introduced external air and by providing multiple oil paths radially. CONSTITUTION:When a work is gripped by a chuck section and a cylinder 1 is rotated, a rotary valve 5 is rotated rogether with a fan 29, the external air flows in an arrow direction V1 from the chuck side on the surface of the cylinder 1 by means of the generated negative pressure, and also the external air flows in an arrow direction V2 from the opposite side through a rotary bearing body to offer a cooling function. Since multiple radial oil paths are provided in the rotary bearing body, more effective cooling function is available.

Description

DETAILED DESCRIPTION OF THE INVENTION The rotary hydraulic cylinder of the conventional device has five rotary cylinders.
If the rotary hydraulic cylinder is rotated at a high speed of 000R◆PGM or higher, the overall temperature of the device will rise due to heat generation in the rotary bearing, causing a problem in the performance of the rotary hydraulic cylinder.

The conventional technology to prevent such a temperature rise is to increase the oil tank capacity and increase the overall circulation amount of hydraulic oil so that it is naturally cooled. ■In order to improve the heat dissipation of heat generating parts and other parts, attach fins to the parts as appropriate to dissipate and cool the parts. ■A cooler should be placed in the middle of the hydraulic oil circuit. However, there are problems such as the equipment becoming larger and more complicated, making it more expensive, and increasing oil leakage.

In order to eliminate the above-mentioned problems, the present applicant first applied for a patent application in 1973.
-52299 was submitted. The present invention further improves this, and in order to further enhance the cooling effect and minimize oil leakage, KL,
Moreover, the overall size and weight of the device can be reduced.

An example of the implementation of the device of the present invention will be described below with reference to the accompanying drawings.

In Figure 1, 1 is the cylinder, 2 is the piston rod, and 3
is a piston fixed on the piston rod 2,
It is slidably fitted into the cavity of the cylinder 1. 5
is a rotary valve that is fitted into the piston rod 2, and a locking mechanism 6 that locks the flow of oil is provided in a part of the inlet.
．． 6' is assembled, and the bolt 7 is attached to the cylinder 1.
It is joined using. 8.9.10 is an O-ring to maintain airtightness.

It is ng.

Reference numeral 11 denotes a guide pin fixed to the piston 3, and either end p or p' of the guide pin is always guided into a guide pin hole 12 provided in the cylinder 1 or the rotary valve 5 (in the illustrated example, on the cylinder side). As a result, free rotation of the piston rod 2 is restricted.

In the illustrated example, the right end of the piston rod 2 is connected to a draw tube to move the jaws (none of which are shown) of the chuck body.

On the other hand, the rotary valve 5 has a two-stage brocade section with 1 and K2.
A sleeve body 13 is provided at the lower stage. There is a sleeve 1 inside the sleeve body 13.
4 is provided as follows. That is, one of the bearings 15 and 15' (15 in the illustrated example) fitted into both ends of the sleeve 14 is brought into direct contact with the inner wall of the sleeve 14,
The other bearing (151 in the illustrated example) is attached to the sleeve cover 1 which is connected to the sleeve body 13 with bolts 16.
It is made to abut against the inner wall of the. A stopper 18 is fixed to the edge of the lower part using bolts 19, and a concave-convex shape having a labyrinth seal structure is formed between the two facing the sleeve cover. Therefore, oil entering from the outside is discharged to the outside from the oil drain groove 20,
Oil leaking from inside the tank is collected through an oil drain groove 21 into a drain reservoir 22 in the IJ+da body 13. At this time, the sleeve cover 17 is provided with an air plug 23 in order to easily and reliably separate and distinguish the discharge and recovery.

Next, if we explain the operation of the piston 3 in the cylinder 1,
This is done as follows. External supply device (not shown)
The hydraulic oil from the oil tank is supplied to the oil supply pipe port 2 of the sleeve body 13.
4, passes through the oil passage 25, passes through the lock mechanism 6, and then the oil passage 26,
The oil is guided to the oil chamber 27, and the piston 3 is moved to the left in the drawing. The drained oil in the oil chamber 27' that is pushed out as the piston 3 moves passes through the lock mechanism 6', the oil passage 25°, and is collected from the drain oil pipe port 241 to an external supply device.

When the forward stroke of the piston is completed and the piston moves to the backward stroke, a switching valve (not shown) is installed so that the aforementioned oil drain pipe port 24' becomes the oil filling pipe port and the oil filling pipe port 24 becomes the oil drain pipe port. The change is made by switching, and the reverse process is performed using a similar reverse path circuit. At this time, a small amount of hydraulic oil is supplied to both side bearings 15.15" through the gap T1r1+1 between the rotary pulp 5 and the sleeve 14, and after lubricating the bearings 15.If)°, it flows into the drain reservoir. 22 and is recovered to an external supply device (oil f1).

Using the hydraulic oil circuit described above, a workpiece (not shown) is gripped by the jaws and the workpiece is machined. When continuing this machining, the thermal energy generated due to the high speed rotation of the rotary pulp 5 is
The hydraulic oil in the oil chambers 26, 26' and 27, 27' is heated to raise the oil temperature. The main sources of thermal energy are ■ Shear heat in the rotating parts of the hydraulic oil, frictional heat of the bearings and agitation heat of the hydraulic oil in the core, and ■ Conversion due to pressure oil leakage of the hydraulic oil. Such as fever.

An increase in oil temperature due to this generated heat reduces the viscosity of the hydraulic oil or causes the piston rod to vibrate slightly. Furthermore, the oil leakage increases and hydraulic energy is lost, and this loss weakens the gripping force of the jaws of the chucking device, causing problems such as deterioration of machining accuracy.

In Japanese Patent Application No. 54-52299, in order to prevent the temperature of the entire device and the oil from rising due to the generated heat, the following measures are taken to prevent the temperature of the entire device and the oil from rising. The position of the rotary pulp 5 to which the fan 29 is attached is the recess of the step Kl of the brocade,
A cylindrical cover 30 having a bent flange Q is attached to the front surface of the fan 29 to allow air to flow into the stepped portion of the brocade along the recess 1.

This allows the outside air to flow from the front surface of the cylinder 1 through the bell-shaped stepped portion Kl of the rotary pulp 5 toward the rear of the sleeve body 13, and since the surface area of the outer circumferential surface becomes wider, the heat dissipation area increases. This is done so that an effective cooling effect can be achieved. Numerals 31 and 32 are bolts for mounting the fan and the cylindrical cover.

In carrying out the above-mentioned implementation, the inside of the cylindrical cover 30 is formed into a hollow structure, and when the heat-absorbing agent is sealed in the hollow inside and circulated, a more effective cooling effect is achieved.

In addition, when the fan 29 is made to have a variable pitch structure, or when the fan ship is fixed on the rotary pulp key stage El or the cylindrical cover 30 is fixed on the fins, the fan 29 can be slid as appropriate within the bored slits 33 and 34. However, by fixing the air gap 35, the gap 35 serving as an air intake port can be changed as appropriate.

One aspect of the present invention is that, in the above-mentioned configuration, the air flows into the rotary bearing body consisting of the piston rod 2, the rotary pulp 5, the sleeve 14, or the sleeve body 13 from the side opposite to the chuck, and is located at the fan 29 position or the cover 30 position. A ventilation passage 3q for cooling the outside air discharged into the shaft is bored, and as the fan 29 rotates, the outside air is forced to pass from the opposite side of the chuck into the rotating bearing body. It will be carried away by someone else.

To explain this mode of implementation, Fig. 2 is a book that mainly considers cooling at the contact surface H between the piston rod 2 and the rotary pulp 5, and shows the cooling in the longitudinal direction on the outer circumferential surface of the piston rod 2. A cooling ventilation passage is provided as a slit 37a of a certain length, and the outside air is passed through the stopper 18.
It flows into the starting end E of the slit 3ma through the introduction hole 39 drilled in the rotary pulp 5 and the introduction hole 39 drilled in the rotary pulp 5, and flows into the exhaust hole 40 drilled in the rotary pulp 5 again from the end E1 of the slit 37a. This allows the fan to pass through to the fan 29 position.

At this time, the exhaust hole 40° may be drilled as shown by the dashed line to allow the exhaust hole to pass through to the front side of the cover 30. Note that the number of the sulins) 3'ia can be provided in any number in the circumferential direction in order to enhance the cold air effect, and the shape thereof is not limited to a slit, but may be an arcuate ring or an annular ring.

FIG. 3 shows an example in which a cooling ventilation passage 37# is bored inside the rotary pulp 5.
Cooling is also achieved at the contact surface LK with 4.

In this example, the exhaust hole 401 is located at the key stage of the rotary pulp 5 and the gap 4 formed between the side wall of the rotary pulp 5 and the side wall of the sleeve body 13.
1 is shown, but it may be drilled toward the fan 29 position or the cover 30 position as in the previous example. Moreover, the number of ventilation passages can also be made arbitrary.

FIG. 4 shows an example in which a cooling ventilation passage 37r is bored in the sleeve body 13, and an introduction hole 39'' is bored in the sleeve cover 17.

Although the cooling ventilation passages have been described as being provided individually on each side, they may be used in appropriate combinations, and these are included within the scope of the present invention. In this manner, in the present apparatus implemented, during work, the outside air is guided in the directions indicated by the arrows, and the internal heat is carried away to the outside for effective cooling. In addition, in the present invention, in addition to the above-mentioned cooling effect, the rotating pulp 5 is
It is possible to effectively prevent oil leakage at the contact portion (F in the first illustrated example) between the key stage portion and the sleeve body 13,
In particular, in the examples shown in FIGS. 2 and 3, experiments conducted by the present inventors have shown that it is more effective to drill a through hole 42 communicating with the end groove f of the labyrinth seal structure. I was hurt by this.

It was also confirmed that no misting phenomenon (fringing effect of the fan) occurred.

On the other hand, in the apparatus of the present invention, by configuring the oil passage block as follows, the cooling effect of the hydraulic oil can be increased and the leakage thereof can be minimized compared to the conventional apparatus.

That is, FIG. 1 is a partially cutaway perspective view of the sleeve 14, and FIG. 6 is a developed plan view showing the arrangement of the oil supply passage and the oil drainage passage within the sleeve.

As seen in this drawing, in the present invention, the oil passage 4 for lubrication is
6 and many oil drainage oil passages 46" 46a 46b
46c , , , 46'a , 46°
A large number of holes are drilled in the radial direction as shown in b 46'c..., and in this case, adjacent lubrication oil passages 4
6 and the drain oil passage 46' are arranged in a staggered relationship, and each oil passage surface on the inner surface of the sleeve is formed with bow-shaped notches s and I.

The feature of the above structure in the present invention is the concave ring 45.4 which becomes the passage for the hydraulic oil to enter and exit from the oil supply pipe port 24 and the oil drain pipe port 24'.
A large number of lubrication oil passages 46a are provided in order to reduce the distance l between the 5° and increase the cooling effect.

46b 46t -* -e -, drain oil passage a6!
g, 46'b.

Even if 46'l... is provided, since they are arranged next to each other in a staggered manner, the distance between each oil passage is made relatively large and leakage of hydraulic oil is reduced. Moreover, the bowstring-shaped notches t and t' have an excellent function and effect in alleviating the impact when the hydraulic oil flows and preventing the deterioration phenomenon in which the oil becomes foamy. In addition, concave ring 45.4
Minimizing the distance ml between the 51 is advantageous in terms of making the entire device smaller and more compact.

On the other hand, an oil passage reservoir 47.47' is bored on the rotary pulp 5 side and communicates with the oil supply passage 46 and the oil drainage passage 46°.
are formed in a crescent shape as shown in the sectional view taken along line XX in FIG. The plurality of cylinders 1 are arranged symmetrically as shown in FIG. In the illustrated example, two holes each are provided, but three holes each may be provided, which is superior in terms of centripetal action directed inward from the axis.

The diagram schematically shows a locking mechanism 6 for hydraulic oil to the cylinder 1.
61, each housing M%Ml has a valve body 6.
0.50' is always applied to valve seat 5 via spring b1.51°
2.52', and when it comes into contact with the former valve seat 52, the oil passage 25 from the oil supply pipe
In this case, the oil passage 26 toward the oil chamber '27 of the cylinder is closed off, and the latter valve body 50'' closes off the space between the oil drain passage 25' and the oil chamber '27 of the cylinder. 53 and 531 are the valve bodies b.
A pilot spool provided at the opposite position between O150° and the valve seat 52.521, and its protrusion 1% l
1 is configured to be able to come into contact with each valve body 50.5α, and the opposite ring surface thereof is configured to communicate with the oil passage 25' on the oil drain pipe side and the oil passage 25 on the oil filling pipe side, respectively. The arrows A, 口, 2, E move the piston rod 2 in the illustrated example to the left (Q direction), and at this time the jaws of the chuck body (not shown) are moved to grip the article. This shows the state in which oil flows, but when the gripping of the article is finished and the supply of hydraulic oil from the oil pipe is stopped, the valve body 50.5σ is closed by the action of the spring 51.5.11. If this state continues for a long time and the oil temperature rises, cylinder 1 will rupture due to internal pressure due to expansion of the core oil, but this device adjusts the sliding resistance R of the pilot spool 53°. In this relationship, the balance with the pressing force W by the spring 51'' is R≧W, so that the valve seat 52'' is not blocked only by the pressing force by the spring 51', and a part of the oil caused by the expansion can be discharged. It is eggplant. The above example is an example of gripping an article by moving the piston rod 2 to the left (Q direction), but conversely, the piston rod 2
To solve the same problem when gripping an article by moving the pilot spool 53 to the right, a similar sliding resistance is applied to the pilot spool 53.

In this case, various known means can be adopted as specific means for imparting sliding resistance to the pilot spool 53.53-, but in this drawing, the purpose is achieved by attaching an O-ring 55. It was designed so that In other detent mechanisms, as shown in the partial view of FIG.
A notch W° (only one side example is shown) is made on the inner circumferential surface of the casing near the position where the 2° is not completely closed, and the spring 5 is attached to the outer circumference of the ring of the pilot spool 53°.
It is also possible to incorporate a ball 57'' which is resiliently repelled at 6', and to engage the ball 57' with the notch 55' to obtain the necessary sliding resistance.

The present invention is constructed as described above, and when the workpiece is gripped by the chuck portion (not shown) and the cylinder 1 rotates, the rotary pulp b accompanying this is transferred to the fan 29.
Due to the negative pressure generated at the fan 29 position,
Outside air V1 flows on the surface of the rotating cylinder 1 from the chuck side as shown by the arrow. On the other hand, from the opposite side, outside air v2 flows into the rotary bearing body as shown by the arrow, and both of these effects produce an effective overall cooling effect. Therefore,
This prevents problems such as heat generation that occurs during high-speed operation, deterioration of the hydraulic oil, and reduction in gripping force due to this heat generation.In addition, there are many oil passages surrounding the piston rod in the rotating bearing body. The fact that they are arranged in the radial direction allows for a more effective cooling effect, less leakage of hydraulic oil, and the entire device can be made smaller and lighter, making it more compact.

[Brief explanation of the drawing]

Figure 1 shows the patent application No. 54+ 522, which was previously proposed by the present applicant.
A vertical cross-sectional view showing the configuration of the rotary fluid pressure cylinder device in No. 99 (however, the oil supply pipe port and oil drain pipe port are shown in the position rotated 90 degrees upward) Fig. 2, Fig. 3, and Fig. Fig. 4 is a partial detailed view of an embodiment of the cooling ventilation passage, Fig. 5 is a partially cutaway perspective view of the sleeve, and Fig. 6 shows the arrangement of the oil supply passage and the oil drainage passage within the sleeve. Developed plan view, Figure 7 is a side view cut along the line X-X in Figure 1, Figure 8 is a partial explanatory diagram showing the locking mechanism for hydraulic oil in the rotating cylinder, and Figure 9 shows the detent mechanism. It is a partial explanatory diagram. 1...Cylinder 2...Piston rod 301. Piston 5061 rotating pulp 661,
,, Lock mechanism 1': L, , Guide pin 13
...Sleeve body 14...Sleeve 17...
・Sleeve body 22... Drain reservoir 24...
Oil supply pipe Next "...Oil drain pipe 256'...Oil passage
g 26'...Oil passage 4.27', oil chamber
290.・Fan 30, Cover 376,
3'7b% 3'7t, -MmidRoha, 39 ・
・Introduction hole button, 40', 4 pin...exhaust hole 46・
...Oil passage for oil supply 461...Oil passage for oil drainage 47a
, 47b, 47'a, 47'b++ll@ Yujimen,
50', , Valve Company, 51', Spring b3.531・L Pilot spool 55.5!31 Q-ring Fig. 7 Fig. 8 Fig. 9

Claims (1)

[Scope of Claims] (1) A rotary hydraulic cylinder consisting of a rotary body containing a reciprocating piston and a rotary bearing body equipped with a hydraulic oil supply path for supplying hydraulic oil to the piston within the rotary body. A cylindrical cover having a flange bent inward from the end line facing the rotating body is attached to the outside of the rotating bearing body so as to cover a part of the outer peripheral surface of the rotating body. , a rotor that rotates with the rotor is installed on the side of the rotor in the enclosed cover, and a piston Lorado on the side of the rotary bearing body integrated with the piston, or a rotary pulp surrounding the piston Lorado, or a rotary pulp surrounding the piston, or a rotor on the outer periphery thereof. A cooling air passage is bored in the sleeve body or the like, and reaches the fan position or the cover position after a certain length in the length direction, and outside air rotates from the side opposite to the rotating body through the cooling air passage. ! 11
1. A rotary fluid pressure cylinder for chucking in a machine tool, characterized in that it is configured to pass through the inside of the receiver and join the outer peripheral surface of the rotating body with outside air flowing toward the rotating shaft bearing body. (2) The rotating bearing body is composed of a piston roller in the center, and surrounding it, in order outward, a rotating nozzle, a sleeve, and a sleeve body. A rotary fluid pressure cylinder for chucking in a machine tool (3) A plurality of oil passage reservoirs with a crescent-shaped cross section are bored in an axially symmetrical direction at three locations along the length of the rotary valve. A rotary fluid pressure series for chucking in a machine tool according to claim 2, characterized in that: ←) For chucking in a machine tool according to claim 2, characterized in that a plurality of oil passages are drilled radially at three locations along the length of the outer circumference of the sleeve. Rotating hydraulic cylinder. (5) A patent claim characterized in that a plurality of cylindrical oil passages are bored in the radial direction on two sides along the length of the outer circumference of the sleeve and are provided in a staggered manner between adjacent comrades. A rotary fluid pressure cylinder for chucking in a machine tool according to item 4.