CN219683968U - Locking device for preventing piston from rotating for motorized spindle - Google Patents

Abstract

The utility model relates to a locking device for preventing a piston from rotating, which comprises a mandrel, wherein a first cylinder body, a second cylinder body and a brake assembly are arranged on the peripheral side wall of the mandrel, the first cylinder body and the second cylinder body are coaxially sleeved on the mandrel, and the first cylinder body, the mandrel and the second cylinder body rotate with the mandrel; the brake assembly comprises a brake disc, a first piston, a second piston and an auxiliary piston, the brake disc is fixedly connected to the mandrel, the first piston and the second piston are arranged on two axial sides of the brake disc in a sliding mode and slide towards the directions approaching or separating from each other, and the auxiliary piston is connected with one side, close to the first piston, of the second piston through a connecting ring; the first piston is provided with a first flange, and the first cylinder body is provided with a first groove for the first flange to slide; the second piston is provided with a second flange, and the second cylinder body is provided with a second groove for the second flange to slide. The utility model has the effects of reducing the risk of piston movement clamping stagnation, simplifying the structure and improving the convenience of assembly.

Description

Locking device for preventing piston from rotating for motorized spindle

Technical Field

The utility model relates to the field of electric spindles, in particular to a locking device for preventing a piston from rotating.

Background

In the field of middle-high end spindle numerical control machine tools, the spindle numerical control machine tool with turning and milling functions capable of being converted mutually can realize complex multitasking processing such as turning, milling, boring, drilling, tapping, multiaxial linkage curved surface processing, inclined plane drilling and the like of rotary parts. The turning and milling of the polyhedron are completed through one-time clamping, and the precision loss caused by secondary or repeated clamping is avoided.

When the spindle is applied to turning, the spindle is required to be in a rotatable state, and when the spindle is applied to milling or tapping, the spindle is required to be in a fixed state, and in order to realize flexible switching between functions, a locking mechanism for braking the rotation of the spindle is required to be arranged for the lathe spindle.

In the related art, the brake mechanism comprises a mandrel which is rotatably arranged in the main shaft, the mandrel is equivalent to the mandrel, a brake disc is fixedly connected to the peripheral side wall of the mandrel, a first piston and a second piston are arranged on two sides of the axial direction of the brake disc, and the first piston and the second piston slide to be in contact with or out of contact with two end surfaces of the brake disc simultaneously in a direction approaching or separating from each other under the pushing of oil pressure so as to realize locking and unlocking. In order to prevent the first piston and the second piston from rotating during braking, conventionally, a plurality of pin holes are formed in the brake disc along the circumferential direction of the brake disc, a connecting pin penetrates into each pin hole, two ends of the length direction of the connecting pin penetrate into the first piston and the second piston respectively, the connecting pins are in sliding connection relative to the brake disc, the first piston and the second piston, and the possibility of piston rotation is reduced due to the combined action of a plurality of connecting pins in the circumference of the brake disc.

However, the connecting pin is connected with the brake disc, the first piston and the second piston at the same time, and the refrigerator axially slides the brake disc, the first piston, the second piston and the plurality of connecting pins, so that the machining requirements of the brake disc, the first piston, the second piston and the plurality of connecting pins are higher, and when the precision is insufficient, the sliding of the first piston and the second piston has the clamping stagnation risk, the braking effect can be influenced, the braking effect can be relieved, and the running stability of the electric spindle is reduced.

Disclosure of Invention

In order to reduce the risk of piston movement clamping stagnation and reduce the influence on braking effect and releasing the braking effect, thereby improving the running stability of the electric spindle, the utility model provides a locking device for preventing the piston from rotating.

The utility model provides a locking device for preventing piston rotation of an electric spindle, which adopts the following technical scheme:

the locking device for preventing the piston from rotating comprises a mandrel, wherein a first cylinder body, a second cylinder body and a brake assembly are arranged on the peripheral side wall of the mandrel, the first cylinder body and the second cylinder body are coaxially sleeved on the mandrel, and the first cylinder body, the mandrel and the second cylinder body rotate with the mandrel;

the brake assembly comprises a brake disc, a first piston, a second piston and an auxiliary piston, wherein the brake disc is fixedly connected to the peripheral side wall of a mandrel through an adjusting gasket, the first piston and the second piston are arranged on two axial sides of the brake disc in a sliding mode, the first piston and the second piston slide towards directions approaching or separating from each other, and the auxiliary piston is fixedly connected to one side, close to the first piston, of the second piston through a connecting ring;

a first flange is connected to one surface of the first piston, which is close to the first cylinder body, and a first groove for the first flange to slide is formed in one surface of the first cylinder body, which is close to the first piston;

a second flange is connected to one surface of the second piston, which is close to the second cylinder body, and a second groove for the second flange to slide is formed in one surface of the second cylinder body, which is close to the first piston;

the auxiliary piston is connected with an auxiliary flange on one side close to the first piston, a containing ring groove is formed in one side, close to the second piston, of the outer peripheral side wall of the first piston, and an auxiliary groove for sliding of the auxiliary flange is formed in one side, far away from the second piston, of the containing ring groove.

Through adopting above-mentioned technical scheme, when first piston slides along the axial of dabber, first flange slides in first recess, when second piston slides along the axial of dabber, the second flange slides in the second recess, auxiliary piston slides in auxiliary recess through the adapter ring when the axial of dabber is followed to the second piston, the connection of connecting pin has been removed, and in the traditional many connecting pins of installing on the brake disc connect first piston, the anti-rotation mode of second piston, adopt the flange card to go into the connected mode of notch between piston and cylinder body, piston and the piston in this scheme, compare in the connecting pin connection mode of brake disc and two pistons simultaneously, the flange slides and plays the guide effect in corresponding recess respectively, under the precision of same machining, the risk of jamming can be reduced, the possibility that blocks and influence braking effect and release braking effect when having reduced the axial of piston along the dabber, thereby the stability and the life-span of electric spindle have been improved.

Further, the length of the first flange is greater than a first braking distance, the depth of the first groove is greater than the length of the first flange, the length of the second flange is greater than a second braking distance, the depth of the second groove is greater than the length of the second flange, the length of the auxiliary flange is greater than the second braking distance, and the depth of the auxiliary groove is greater than the length of the auxiliary flange.

By adopting the technical scheme, as the length of the first flange is longer than the first braking distance, and the depth of the first groove is longer than the length of the first flange, when the first piston slides along the axial direction of the mandrel, the possibility that the first flange slides to be separated from the first groove is reduced; since the length of the second flange is greater than the second braking distance, the depth of the second groove is greater than the length of the second flange, thereby reducing the possibility of the second flange sliding out of the second groove when the second piston slides along the axial direction of the mandrel; because the length of the auxiliary flange is greater than the second braking distance, the depth of the auxiliary groove is greater than the second flange length, so when the auxiliary piston slides along the axial direction of the mandrel along with the second piston, the possibility that the auxiliary flange slides to be separated from the auxiliary groove is reduced; the stability of the overall movement of the piston is improved.

Further, a first chamber is arranged in the first cylinder body, the first piston slides in the first chamber, a second chamber is arranged in the second cylinder body, the second piston slides in the second chamber, an auxiliary chamber communicated with the containing ring groove is also arranged in the first cylinder body, the auxiliary piston slides in the chamber communicated with the containing ring groove, and the first chamber, the second chamber, the auxiliary chamber and the containing ring groove are all communicated;

a first oil cavity and a second oil cavity which are communicated with the first cavity are arranged in the first cylinder body, a first oil hole is formed in the peripheral side wall of the first cylinder body, the first oil hole is communicated with the first oil cavity through a first oil way, the first oil hole is communicated with the second oil cavity through a second oil way, a limiting ring plate is coaxially connected to one side, close to the second piston, of the inner peripheral side wall of the first piston, the first oil way is located at the containing ring groove, and the second oil way is located at the limiting ring plate;

a third oil cavity communicated with the second cavity is arranged in the second cylinder body, a second oil hole is formed in the peripheral side wall of the second cylinder body, and the second oil hole is communicated with the third oil cavity through a third oil way;

an auxiliary oil hole is formed in the peripheral side wall of the first cylinder body, and the auxiliary oil hole is communicated with the auxiliary cavity.

Through the technical scheme, when the mandrel is required to be locked, a first strand of hydraulic oil is pumped into the first oil hole at high pressure, a second strand of hydraulic oil is pumped into the second oil hole at high pressure, the first strand of hydraulic oil enters the first oil cavity through the first oil way, enters the second oil cavity through the second oil way and then pushes the first piston to slide towards a direction close to the brake disc, and meanwhile, the second strand of hydraulic oil enters the third oil cavity through the third oil way and then pushes the second piston to slide towards the direction close to the brake disc, so that the brake disc is synchronously abutted against and locked by the first piston and the second piston on two axial sides of the brake disc, the auxiliary piston slides along with the second piston at the moment, and the auxiliary piston slides in the auxiliary chamber and the chamber communicated with the containing ring groove;

when the locking is required to be released, a third strand of hydraulic oil is pumped into the auxiliary oil hole from a high pressure, and after entering the auxiliary oil cavity and the containing ring groove through the auxiliary oil way, the third strand of hydraulic oil pushes the auxiliary piston and the first piston simultaneously, so that the first piston slides towards the direction away from the brake disc, and simultaneously drives the second piston to slide towards the direction away from the brake disc through the auxiliary piston, thereby releasing the locking state.

Further, the first flange is the arc setting and the radian is consistent with the internal diameter radian of first piston, the second flange is the arc setting and the radian is consistent with the external diameter radian of second piston, the auxiliary flange is the arc setting and the radian is consistent with the internal diameter radian of auxiliary piston.

Through adopting above-mentioned technical scheme, improved the complex smoothness nature between first flange and the first recess, the complex smoothness nature between second flange and the second recess, the complex smoothness nature between auxiliary flange and the auxiliary recess.

Further, the first flange is located at two radial sides of the first piston, the second flange is located at two radial sides of the second piston, and the auxiliary flange is located at two radial sides of the auxiliary piston.

By adopting the technical scheme, the sliding stability of the first piston and the second piston is improved.

Further, the second flanges are arranged in a staggered manner on the first flanges and the second flanges, and the connecting lines of the two first flanges are perpendicular to the connecting lines of the two second flanges.

By adopting the technical scheme, the stability of the overall movement of the piston is further improved.

Further, a balance oil path is communicated between the first oil hole and the second oil hole.

By adopting the technical scheme, the pressures born by the first piston and the second piston are balanced, and the stability of the braking effect is improved.

Further, a first sealing ring is arranged on the first piston, and the first sealing ring is positioned at the contact position of the first piston and the first cylinder body;

the second piston is provided with a second sealing ring, and the second sealing ring is positioned at the contact position of the second piston and the second cylinder body;

a third sealing ring is arranged on the auxiliary piston and is positioned at the contact position of the auxiliary piston and the first cylinder body;

the auxiliary piston is provided with a fourth sealing ring, and the fourth sealing ring is positioned at the contact position of the auxiliary piston and the inner wall of the containing ring groove.

By adopting the technical scheme, the tightness between the first piston and the first cylinder body, between the second piston and the second cylinder body, between the auxiliary piston and the first cylinder body and between the auxiliary piston and the first piston is improved.

In summary, the present utility model includes at least one of the following beneficial technical effects:

1. in the scheme, the connection mode that the flanges are clamped into the notch is adopted between the piston and the cylinder body and between the piston and the piston, and compared with the connection mode that the connecting pins are used for simultaneously connecting the brake disc and the two pistons, the flanges slide in the corresponding grooves respectively to play a role in guiding, and under the same machining precision, the clamping risk can be reduced, namely the possibility that the piston is clamped when sliding along the axial direction of the mandrel to influence the braking effect and release the braking effect is reduced, so that the running stability and the safety reliability of the electric spindle are improved, and the service life of the electric spindle is further prolonged;

2. the connecting pins are not required to be installed along the circumferential direction of the brake disc, and only the flange and the groove are required to be installed correspondingly, so that the complex installation process of one-to-one correspondence of the connecting pins and the pin holes is avoided, and the operation is simple and convenient;

3. the locking brake and unlocking of the mandrel can be performed stably and timely.

Drawings

Fig. 1 is an overall exploded view of a piston-rotation-preventing locking device for an electric spindle according to an embodiment of the present utility model.

Fig. 2 is a schematic overall cross-sectional view of a piston-rotation-preventing locking device for an electric spindle according to an embodiment of the present utility model.

Fig. 3 is a schematic view for showing the structure of the first cylinder in the embodiment of the present utility model.

Fig. 4 is a schematic view for showing the structure of the first piston in the embodiment of the present utility model.

Fig. 5 is a schematic view for showing the structure of the auxiliary piston in the embodiment of the present utility model.

Fig. 6 is a schematic diagram for showing the structure of the second piston in the embodiment of the present utility model.

Fig. 7 is a schematic view for showing the structure of the second cylinder in the embodiment of the present utility model.

Fig. 8 is a schematic view showing the configuration of the first piston, the auxiliary piston, and the second piston in cooperation with each other in the embodiment of the present utility model.

Reference numerals illustrate: 1. a mandrel; 2. a first cylinder; 21. a first chamber; 22. an auxiliary chamber; 23. a first oil chamber; 231. a first oil passage; 24. a second oil chamber; 241. a second oil path; 25. a first oil hole; 26. an auxiliary oil hole; 3. a second cylinder; 31. a second chamber; 32. a third oil chamber; 321. a third oil passage; 33. a second oil hole; 4. a bearing; 5. a brake assembly; 51. a brake disc; 511. adjusting the gasket; 52. a first piston; 521. a first flange; 522. a first groove; 523. a first seal ring; 53. a second piston; 531. a second flange; 532. a second groove; 533. a second seal ring; 54. an auxiliary piston; 541. an auxiliary flange; 542. an auxiliary groove; 543. a third seal ring; 544. a fourth seal ring; 6. a connecting ring; 7. a receiving ring groove; 8. a limiting ring plate; 81. a fifth seal ring; 9. balance oil circuit; 91. and a sixth sealing ring.

Detailed Description

The utility model is described in further detail below with reference to fig. 1-8.

The embodiment of the utility model discloses a locking device for preventing a piston from rotating, which is used for an electric spindle.

Referring to fig. 1-8, a locking device for an electric spindle that prevents piston rotation comprises a rotatable spindle 1, the spindle 1 being coaxially rotatably arranged in the electric spindle by means of a drive arranged in the electric spindle. The periphery wall of the mandrel 1 is provided with a first cylinder body 2, a second cylinder body 3, a bearing 4 and a brake assembly 5, the first cylinder body 2 and the second cylinder body 3 are coaxially sleeved on the mandrel 1, the bearing 4 is sleeved on the mandrel 1, the first cylinder body 2 and the mandrel 1, the second cylinder body 3 are fixedly connected with the fixing part of the bearing 4, so that the first cylinder body 2 and the second cylinder body 3 are relatively fixed, and the first cylinder body 2 is in rotary connection with the mandrel 1, and the second cylinder body 3 and the mandrel 1.

The brake assembly 5 comprises a brake disc 51, a first piston 52, a second piston 53 and an auxiliary piston 54, wherein the brake disc 51 is fixedly connected to the peripheral side wall of the mandrel 1 through an adjusting gasket 511, and the brake disc 51 and the mandrel 1 are coaxially arranged. The first piston 52 and the second piston 53 are slidably provided on both sides in the axial direction of the brake disc 51, and the first piston 52 and the second piston 53 are slid in directions toward or away from each other. A first braking distance exists between the first piston 52 and the end face on one side of the brake disc 51, a second braking distance exists between the second piston 53 and the end face on the other side of the brake disc 51, and the first braking distance is consistent with the second braking distance, so that the first piston 52 and the second piston 53 can synchronously brake in place.

The auxiliary piston 54 is fixedly connected with one side, close to the first piston 52, of the second piston 53 through the connecting ring 6, and the connecting ring 6 is integrally formed on the second piston 53, so that the connecting effect of a traditional connecting pin is avoided.

The side, close to the second piston 53, of the outer peripheral side wall of the first piston 52 is provided with a containing ring groove 7, a first chamber 21 is arranged in the first cylinder body 2, the first piston 52 slides in the first chamber 21, the second cylinder body 3 is provided with a second chamber 31, and the second piston 53 slides in the second chamber 31. The first cylinder body 2 is also internally provided with an auxiliary chamber 22 communicated with the containing ring groove 7, the auxiliary piston 54 is slidably arranged in the chamber communicated with the containing ring groove 7 and the auxiliary chamber 22, the first chamber 21 and the second chamber 31 are communicated, and the auxiliary chamber 22 and the containing ring groove 7 are all communicated.

And a limiting ring plate 8 is coaxially and integrally formed on one side, close to the second piston 53, of the inner peripheral side wall of the first piston 52, and the distance between one surface, far away from the second piston 53, of the limiting ring plate 8 and the inner wall, located at the second oil path 241, of the first chamber 21 is larger than a first braking distance, so that the first piston 52 is ensured to have enough sliding space while limiting and guiding.

A first oil chamber 23 and a second oil chamber 24 which are communicated with the first chamber 21 are arranged in the first cylinder body 2, a first oil hole 25 is formed in the peripheral side wall of the first cylinder body 2, the first oil hole 25 is communicated with the first oil chamber 23 through a first oil path 231, and the first oil hole 25 is communicated with the second oil chamber 24 through a second oil path 241. The first oil path 231 is located at the receiving ring groove 7 and extends to a side of the first piston 52 away from the second piston 53, and the second oil path 241 is located at the retainer ring plate 8 and extends to a side of the first piston 52 away from the second piston 53.

A third oil chamber 32 communicated with the second chamber 31 is arranged in the second cylinder body 3, a second oil hole 33 is formed in the peripheral side wall of the second cylinder body 3, and the second oil hole 33 is communicated with the third oil chamber 32 through a third oil path 321.

An auxiliary oil hole 26 is formed in the peripheral side wall of the first cylinder body 2, the auxiliary oil hole 26 is communicated with the auxiliary chamber 22, and hydraulic oil in the auxiliary oil hole 26 flows into the auxiliary chamber 22 and the accommodating ring groove 7 at the same time.

The balance oil path 9 is communicated between the first oil hole 25 and the second oil hole 33, so that oil pressure is balanced, the pressures received by the first piston 52 and the second piston 53 are balanced, and the stability of a braking effect is improved.

When the mandrel 1 needs to be locked, a first strand of hydraulic oil is pumped into the first oil hole 25 at high pressure, a second strand of hydraulic oil is pumped into the second oil hole 33 at high pressure, the first strand of hydraulic oil enters the first oil cavity 23 through the first oil way 231, enters the second oil cavity 24 through the second oil way 241 and pushes the first piston 52 to slide towards a direction approaching the brake disc, meanwhile, the second strand of hydraulic oil enters the third oil cavity 32 through the third oil way 321 and pushes the second piston 53 to slide towards the direction approaching the brake disc, so that the brake disc is synchronously abutted and locked by the first piston 52 and the second piston 53 on two axial sides of the brake disc, the auxiliary piston 54 slides along with the second piston 53 at the moment, and the auxiliary piston 54 slides in a cavity communicated with the auxiliary cavity 22 and the containing ring groove 7;

when the locking needs to be released, a third strand of hydraulic oil is pumped from the auxiliary oil hole 26 at high pressure, and after entering the auxiliary oil cavity and the containing ring groove 7 through the auxiliary oil way, the third strand of hydraulic oil pushes the auxiliary piston 54 and the first piston 52 simultaneously, so that the first piston 52 slides towards the direction away from the brake disc, and meanwhile, the auxiliary piston 54 drives the second piston 53 to slide towards the direction away from the brake disc, so that the locking state is released.

The inner peripheral side wall of the auxiliary piston 54 is attached to the inner wall of the accommodating ring groove 7, the distance between the surface of the auxiliary piston 54 far away from the second piston 53 and the inner wall of the surface of the accommodating ring groove 7 far away from the second piston 53 is a sliding distance, and the sliding distance is equal to the sum of the first braking distance and the second braking distance, so that when the first piston 52 and the second piston 53 synchronously brake in place, the first piston 52 is abutted against the auxiliary piston 54, and at the moment, the first piston 52 and the second piston 53 are abutted against each other through the auxiliary piston 54, so that the movement along the axial direction of the mandrel 1 is difficult to occur, and the stability of the braking effect is improved.

The first flange 521 is fixedly connected to one surface of the first piston 52, which is close to the first cylinder body 2, and the first flange 521 is arranged in an arc shape, and the radian of the first flange 521 is consistent with the radian of the inner diameter of the first piston 52. The first flange 521 is located on both sides in the radial direction of the first piston 52. The first cylinder 2 is provided with a first groove 522 for sliding the first flange 521 on a surface close to the first piston 52, and when the first piston 52 slides along the axial direction of the mandrel 1, the first flange 521 slides in the first groove 522.

The second flange 531 is fixedly connected to the surface, close to the second cylinder body 3, of the second piston 53, and the second flange 531 is arranged in an arc shape, and the radian of the second flange is consistent with that of the outer diameter of the second piston 53. The second flange 531 is located on both sides in the radial direction of the second piston 53. The second cylinder 3 is provided with a second groove 532 on one surface close to the first piston 52 for sliding the second flange 531, and when the second piston 53 slides along the axial direction of the mandrel 1, the second flange 531 slides in the second groove 532.

An auxiliary flange 541 is fixedly connected to one surface of the auxiliary piston 54, which is close to the first piston 52, and the auxiliary flange 541 is arranged in an arc shape, and the radian of the auxiliary flange is consistent with the radian of the inner diameter of the auxiliary piston 54. The second flange 531 is located on both sides in the radial direction of the second piston 53. An auxiliary groove 542 is formed in the surface of the accommodating ring groove 7 away from the second piston 53, in which the auxiliary flange 541 slides in the auxiliary groove 542 when the auxiliary piston 54 slides along the axial direction of the mandrel 1.

Compared with the traditional anti-rotation mode that a plurality of connecting pins are arranged on a brake disc to connect a first piston 52 and a second piston 53, in the scheme, a flange clamping notch is adopted between the piston and a cylinder body and between the piston and the piston, and compared with the connecting mode that the connecting pins are simultaneously connected with the brake disc and two pistons, the flange respectively slides in corresponding grooves to play a guiding role, and under the same machining precision, the clamping stagnation risk can be reduced, namely the possibility that the piston is clamped when sliding along the axial direction of a mandrel 1 to influence the braking effect and release the braking effect is reduced, so that the running stability and the safety and reliability of the electric spindle are improved, and the service life of the electric spindle is further prolonged. Moreover, this technical scheme has reduced spare part quantity and processing degree of difficulty, does not need to install many connecting pins along the circumference of brake disc, has simplified the structure, only needs to correspond the installation with flange and recess, has avoided the loaded down with trivial details installation of connecting pin and a plurality of pinhole one-to-one, easy and simple to handle.

The length of the first flange 521 is greater than the first braking distance, and the depth of the first groove 522 is greater than the length of the first flange 521, reducing the likelihood that the first flange 521 will slide out of the first groove 522 when the first piston 52 slides in the axial direction of the spindle 1. The length of the second flange 531 is greater than the second braking distance, and the depth of the second groove 532 is greater than the length of the second flange 531, reducing the likelihood that the second flange 531 will slide out of the second groove 532 when the second piston 53 slides in the axial direction of the spindle 1. The length of the auxiliary flange 541 is greater than the second braking distance, and the depth of the auxiliary groove 542 is greater than the length of the auxiliary flange 541, reducing the likelihood that the auxiliary flange 541 will slide out of the auxiliary groove 542 as the auxiliary piston 54 slides along the axial direction of the spindle 1 with the second piston 53. The stability of the overall movement of the piston is improved.

The second flanges 531 are staggered with the first flanges 521 and the second flanges 531, and the connecting lines of the two first flanges 521 are vertical to the connecting lines of the two second flanges 531, so that the stability of the overall movement of the piston is further improved.

The inner peripheral side wall and the outer peripheral side wall of the first piston 52 are respectively provided with a first sealing ring 523, the first sealing rings 523 and the mandrel 1 are coaxially arranged, the inner peripheral side wall and the outer peripheral side wall of the first piston 52 are respectively provided with a first sealing ring groove for the first sealing rings 523 to clamp, and the first sealing rings 523 are positioned at the contact part of the first piston 52 and the first cylinder body 2, so that the tightness between the first piston 52 and the first cylinder body 2 is improved.

The second sealing ring 533 is arranged on the inner peripheral side wall and the outer peripheral side wall of the second piston 53, the second sealing ring 533 and the mandrel 1 are coaxially arranged, the second sealing ring grooves for clamping the second sealing ring 533 are formed in the inner peripheral side wall and the outer peripheral side wall of the second piston 53, the second sealing ring 533 is located at the contact position of the second piston 53 and the second cylinder 3, and the tightness between the second piston 53 and the second cylinder 3 is improved.

The third sealing ring 543 is arranged on the outer peripheral side wall of the auxiliary piston 54, the third sealing ring 543 and the mandrel 1 are coaxially arranged, the third sealing ring groove for clamping the third sealing ring 543 is formed in the outer peripheral side wall of the auxiliary piston 54, the third sealing ring 543 is located at the contact position of the auxiliary piston 54 and the first cylinder body 2, and the sealing performance between the auxiliary piston 54 and the first cylinder body 2 is improved.

The fourth sealing ring 544 is arranged on the inner peripheral side wall of the auxiliary piston 54, the fourth sealing ring 544 and the mandrel 1 are coaxially arranged, the fourth sealing ring groove for clamping the fourth sealing ring 544 is formed in the inner peripheral side wall of the auxiliary piston 54, the fourth sealing ring 544 is located at the contact position of the auxiliary piston 54 and the inner wall of the containing ring groove 7, and the sealing performance between the auxiliary piston 54 and the first piston 52 is improved.

The fifth sealing ring 81 is arranged on the inner peripheral side wall of the limiting ring plate 8, the fifth sealing ring 81 and the mandrel 1 are coaxially arranged, the fifth sealing ring groove for clamping the fifth sealing ring 81 is formed in the inner peripheral side wall of the limiting ring plate 8, the fifth sealing ring 81 is located at the contact position of the limiting ring plate 8 and the first cylinder body 2, and the sealing performance between the first piston 52 and the first cylinder body 2 is further improved.

The end face, close to one side of the first cylinder body 2, of the second cylinder body 3 is provided with the sixth sealing ring 91, the second cylinder body 3 is provided with the fifth sealing ring groove for clamping the sixth sealing ring 91, the sixth sealing ring 91 is located at the contact position of the second cylinder body 3 and the first cylinder body 2, the sixth sealing ring 91 is located at the balance oil path 9, and the tightness of the balance oil path 9 between the second cylinder body 3 and the first cylinder body 2 is improved.

The embodiment of the utility model provides an implementation principle of a locking device for preventing piston rotation of an electric spindle, which comprises the following steps: when the spindle 1 needs to be locked, the first hydraulic oil is pumped into the first oil hole 25 at high pressure, the second hydraulic oil is pumped into the second oil hole 33 at high pressure, the first hydraulic oil enters the first oil cavity 23 through the first oil passage 231 and enters the second oil cavity 24 through the second oil passage 241, and then the first piston 52 is pushed to slide towards the direction approaching the brake disc, (in the process, the first flange 521 slides in the first groove 522 to prevent the first piston 52 from rotating), and meanwhile, the second hydraulic oil enters the third oil cavity 32 through the third oil passage 321 and then pushes the second piston 53 to slide towards the direction approaching the brake disc, so that the brake disc is synchronously abutted and locked by the first piston 52 and the second piston 53 at both axial sides of the second piston 53, and at the moment, the auxiliary piston 54 slides along with the second piston 53, namely the auxiliary piston 54 slides in the auxiliary chamber 22 and the chamber communicated with the containing ring groove 7, (in the process, the second flange 531 slides in the second groove 532 to prevent the second piston 53 from rotating and the auxiliary flange 541 from sliding in the auxiliary groove 542 to prevent the auxiliary piston 54 from rotating.

When the locking needs to be released, the third hydraulic oil is pumped into the auxiliary oil hole 26 at a high pressure, and after entering the auxiliary oil cavity and the containing ring groove 7 through the auxiliary oil path, the third hydraulic oil pushes the auxiliary piston 54 and the first piston 52 at the same time, so that the first piston 52 slides in a direction away from the brake disc, (in the process, the first flange 521 slides in the first groove 522 to prevent the first piston 52 from rotating), and meanwhile, the auxiliary piston 54 drives the second piston 53 to slide in a direction away from the brake disc, (in the process, the second flange 531 slides in the second groove 532 to prevent the second piston 53 from rotating, the auxiliary flange 541 slides in the auxiliary groove 542 to prevent the auxiliary piston 54 from rotating), so that the locking state is released.

The above embodiments are not intended to limit the scope of the present utility model, so: all equivalent changes in structure, shape and principle of the utility model should be covered in the scope of protection of the utility model.

Claims (8)

1. A locking device for preventing piston gyration of electricity main shaft, its characterized in that: the device comprises a mandrel (1), wherein a first cylinder body (2), a second cylinder body (3) and a brake assembly (5) are arranged on the peripheral side wall of the mandrel (1), the first cylinder body (2) and the second cylinder body (3) are coaxially sleeved on the mandrel (1), and the first cylinder body (2) and the mandrel (1), and the second cylinder body (3) and the mandrel (1) rotate;

the brake assembly (5) comprises a brake disc (51), a first piston (52), a second piston (53) and an auxiliary piston (54), wherein the brake disc (51) is fixedly connected to the peripheral side wall of the mandrel (1) through an adjusting gasket (511), the first piston (52) and the second piston (53) are arranged on two axial sides of the brake disc (51) in a sliding mode, the first piston (52) and the second piston (53) slide towards directions approaching or separating from each other, and the auxiliary piston (54) is fixedly connected to one side, close to the first piston (52), of the second piston (53) through a connecting ring (6);

a first flange (521) is connected to one surface of the first piston (52) close to the first cylinder body (2), and a first groove (522) for sliding the first flange (521) is formed in one surface of the first cylinder body (2) close to the first piston (52);

a second flange (531) is connected to one surface of the second piston (53) close to the second cylinder body (3), and a second groove (532) for sliding the second flange (531) is formed in one surface of the second cylinder body (3) close to the first piston (52);

an auxiliary flange (541) is connected to one side, close to the first piston (52), of the auxiliary piston (54), a containing ring groove (7) is formed in one side, close to the second piston (53), of the outer peripheral side wall of the first piston (52), and an auxiliary groove (542) for sliding of the auxiliary flange (541) is formed in one side, far away from the second piston (53), of the containing ring groove (7).

2. A piston-rotation-preventing locking device for an electric spindle as claimed in claim 1, wherein: the length of the first flange (521) is greater than a first braking distance, the depth of the first groove (522) is greater than the length of the first flange (521), the length of the second flange (531) is greater than a second braking distance, the depth of the second groove (532) is greater than the length of the second flange (531), the length of the auxiliary flange (541) is greater than the second braking distance, and the depth of the auxiliary groove (542) is greater than the length of the auxiliary flange (541).

3. A piston-rotation-preventing locking device for an electric spindle as claimed in claim 1, wherein: a first chamber (21) is arranged in the first cylinder body (2), the first piston (52) is positioned in the first chamber (21) and slides in the first chamber, a second chamber (31) is arranged in the second cylinder body (3), the second piston (53) is positioned in the second chamber (31) and slides in the second chamber, an auxiliary chamber (22) communicated with the containing ring groove (7) is also arranged in the first cylinder body (2), the auxiliary piston (54) is arranged in the auxiliary chamber (22) and the chamber communicated with the containing ring groove (7) in a sliding manner, and the first chamber (21), the second chamber (31) and the auxiliary chamber (22) are communicated with each other and the containing ring groove (7);

a first oil cavity (23) and a second oil cavity (24) which are communicated with the first cavity (21) are arranged in the first cylinder body (2), a first oil hole (25) is formed in the peripheral side wall of the first cylinder body (2), the first oil hole (25) is communicated with the first oil cavity (23) through a first oil way (231), the first oil hole (25) is communicated with the second oil cavity (24) through a second oil way (241), a limiting ring plate (8) is coaxially connected to one side, close to the second piston (53), of the inner peripheral side wall of the first piston (52), the first oil way (231) is located at the containing ring groove (7), and the second oil way (241) is located at the limiting ring plate (8);

a third oil cavity (32) communicated with the second cavity (31) is arranged in the second cylinder body (3), a second oil hole (33) is formed in the peripheral side wall of the second cylinder body (3), and the second oil hole (33) is communicated with the third oil cavity (32) through a third oil way (321);

an auxiliary oil hole (26) is formed in the peripheral side wall of the first cylinder body (2), and the auxiliary oil hole (26) is communicated with the auxiliary cavity (22).

4. A piston-rotation-preventing locking device for an electric spindle as claimed in claim 1, wherein: the first flange (521) is in an arc-shaped arrangement and the radian is consistent with the radian of the inner diameter of the first piston (52), the second flange (531) is in an arc-shaped arrangement and the radian is consistent with the radian of the outer diameter of the second piston (53), and the auxiliary flange (541) is in an arc-shaped arrangement and the radian is consistent with the radian of the inner diameter of the auxiliary piston (54).

5. A piston-rotation-preventing locking device for an electric spindle as claimed in claim 1, wherein: the first flange (521) is located on both sides in the radial direction of the first piston (52), the second flange (531) is located on both sides in the radial direction of the second piston (53), and the auxiliary flange (541) is located on both sides in the radial direction of the auxiliary piston (54).

6. The anti-piston-rotation locking device for an electric spindle of claim 5, wherein: the second flanges (531) are staggered between the first flanges (521) and the second flanges (531), and the connecting line of the two first flanges (521) is perpendicular to the connecting line of the two second flanges (531).

7. A piston-rotation-preventing locking device for an electric spindle as claimed in claim 3, wherein: a balance oil way (9) is communicated between the first oil hole (25) and the second oil hole (33).

8. A piston-rotation-preventing locking device for an electric spindle as claimed in claim 1, wherein: a first sealing ring (523) is arranged on the first piston (52), and the first sealing ring (523) is positioned at the contact position of the first piston (52) and the first cylinder body (2);

a second sealing ring (533) is arranged on the second piston (53), and the second sealing ring (533) is positioned at the contact position of the second piston (53) and the second cylinder body (3);

a third sealing ring (543) is arranged on the auxiliary piston (54), and the third sealing ring (543) is positioned at the contact position of the auxiliary piston (54) and the first cylinder body (2);

a fourth sealing ring (544) is arranged on the auxiliary piston (54), and the fourth sealing ring (544) is positioned at the contact position of the auxiliary piston (54) and the inner wall of the containing ring groove (7).