CN106438755A - Spit type springless overrunning clutch - Google Patents

Abstract

A split springless overrunning clutch of the present invention comprises a clutch body and a clutch cap, wherein the clutch body is mounted on a hydraulic motor shaft and rotates synchronously with the hydraulic motor shaft, and the clutch cap is mounted on a motor shaft and rotates synchronously with the motor shaft ;The main body of the clutch includes a cam, a support ring and N rolling rods. The cam is located in the middle of the support ring, and the N rolling rods are located outside the cam, evenly distributed along the edge of the support ring. area and N non-working areas, the outer surface of each non-working area matches the inner surface of the edge of the support ring, each working area includes an engagement area and a separation area, and the engagement area and separation area are connected by a transition slope, rolling rods Contact with the meshing area realizes the engagement of the clutch body and the clutch cap, and the contact between the roller rod and the separation area realizes separation. This clutch has no return spring, and relies on the inertia of the ball and the relative movement with the cam to achieve engagement and release. The structure is simple and the reliability is high. , Easy to disassemble and use.

Description

A Split Type Springless Overrunning Clutch

technical field

The invention relates to a split type overrunning clutch, in particular to a split type springless overrunning clutch.

Background technique

Most of the existing overrunning clutches have an integrated structure, which is suitable for occasions where the driving and driven shafts are located in a single component that is not often disassembled. For the occasions where the driving and driven shafts belong to two independent components, it is inconvenient to apply; the existing overrunning clutch Clutches mostly use return springs with complex structures, resulting in low reliability.

The new-generation launch vehicle servo mechanism integrates two modes of ground testing and space flight. The driving components of the two modes are electric motors and hydraulic motors. In order to realize automatic switching between the two modes, and in the space flight mode To achieve the transmission of the output power of the hydraulic motor, a new type of split overrunning clutch must be designed.

Therefore, the model requirements put forward new requirements for the development of overrunning clutches: the main and driven shafts belong to two independent components, and the overrunning clutches should have high reliability.

Contents of the invention

The purpose of the present invention is to overcome the above-mentioned deficiencies in the prior art, and provide a split type springless overrunning clutch, which has no return spring, and relies on the inertia of the ball and the relative movement with the cam to achieve engagement and release, with a simple structure and high reliability. High, easy to disassemble and use, suitable for occasions where the driving shaft and the driven shaft belong to two components.

Above-mentioned purpose of the present invention is mainly achieved through the following technical solutions:

A split-type springless overrunning clutch, including a clutch body and a clutch cap, wherein the clutch body is fixedly mounted on the hydraulic motor shaft and rotates synchronously with the hydraulic motor shaft, and the clutch cap is fixedly mounted on the motor shaft and rotates synchronously with the motor shaft The main body of the clutch includes a cam, a support ring and N rolling rods, wherein the cam is located in the middle of the support ring, and the N rolling rods are located outside the cam and are evenly distributed along the edge of the support ring. The cam has a circular structure, and the circular structure N working areas and N non-working areas are alternately distributed on the outer surface. The outer surface of each non-working area matches the inner surface of the edge of the support ring. Each working area includes an engagement area and a separation area. Between the engagement area and the separation area The contact between the rolling rod and the meshing area realizes the engagement of the clutch body and the clutch cap, and the contact between the rolling rod and the separation area realizes the separation of the clutch body and the clutch cap, wherein N is a positive integer, and N≥3.

In the above-mentioned split-type springless overrunning clutch, both the meshing area and the disengaging area are planes.

In the above-mentioned split type springless overrunning clutch, the two planes of the meshing area and the disengaging area are parallel.

In the above-mentioned split-type springless overrunning clutch, the included angle between the transition slope and the separation zone plane is 120°-150°.

In the above-mentioned split-type springless overrunning clutch, the included angle between the transition slope and the separation zone plane is 130°-140°.

In the above-mentioned split type springless overrunning clutch, the supporting ring is a ring structure, and N blind holes are evenly distributed on the edge of the ring structure for placing N rolling bars. The bottom of the ring structure is a stepped hole, and the cam is placed on the in the step hole and supported by the step.

In the split-type springless overrunning clutch, the clutch body further includes a cover plate and rivets, wherein the cover plate encapsulates the cam and the roller inside the support ring, and the cover plate and the edge of the support ring are fixedly connected by rivets.

In the split-type springless overrunning clutch, the ratio of the wrap angle α of the meshing area to the center of the circle and the wrap angle β of the disengagement area to the center of the circle satisfies: α:β=0.7˜0.9:1.

In the split-type springless overrunning clutch, the ratio of the wrap angle δ of each non-working area to the center of the circle and the wrap angle α of the meshing area to the center of the circle satisfies: δ:α=0.8-0.9:1.

In the above-mentioned split type springless overrunning clutch, the main body of the clutch is installed on the shaft of the hydraulic motor, the axial positioning is realized by the shaft shoulder, the axial direction is fixed by the elastic ring, and the transmission is carried out by two flat keys symmetrically arranged along the circumferential direction; The clutch cap is mounted on the motor shaft through a spline, axially positioned through a washer, and axially fixed through an elastic circlip.

Compared with the prior art, the present invention has the following beneficial effects:

(1), split type springless overrunning clutch of the present invention, its power input end (clutch) and output end (clutch cap) adopt split type structure, are respectively arranged on the driving element and driven element, along with the assembling and dismounting of element Automatically realize assembly and separation, adopts no spring structure, relies on the inertia of the ball and the relative movement with the cam to realize the meshing and loosening, the structure is simple, and the reliability is high;

(2), the overrunning clutch of the present invention adopts a split structure, which is easy to disassemble and use. The clutch part is installed on the output shaft of the active element, and the clutch cap part is installed on the input shaft of the driven element. The two elements are produced separately and managed separately, without Separately installed and combined, it is automatically installed in place with the installation of the two components, which is convenient for disassembly, use and management, and is suitable for occasions where the driving shaft and the driven shaft belong to two components;

(3), N working areas and N non-working areas are alternately distributed on the circular outer surface of the cam in the overrunning clutch of the present invention, and the outer surface of each non-working area cooperates with the inner surface of the edge of the supporting ring, and each working area includes The meshing area and the disengaging area are connected by a transition slope. The present invention provides the optimized shape and size of the engaging area and the disengaging area through theoretical calculation and a large number of experimental verifications, and significantly improves the clutch body and clutch cap. The reliability of the engagement, while realizing the quick engagement and quick disengagement of the clutch body and the clutch cap.

(4) The split-type springless overrunning clutch of the present invention has been successfully applied in a new generation of launch vehicle servo mechanisms, and related technical achievements can also be extended and applied to civilian products and other fields.

Description of drawings

Fig. 1 is the installation structure schematic diagram of clutch main body and clutch cap of the present invention;

Fig. 2 is a structural schematic diagram of the main body of the clutch of the present invention, wherein Fig. 2a is a front view of the main body of the clutch, Fig. 2b is a sectional view along A-A, and Fig. 2c is a sectional view along B-B;

Fig. 3 is a schematic diagram of the relative position of the clutch body and the clutch cap in the engaged state of the present invention;

Fig. 4 is a schematic diagram of the relative position of the clutch body and the clutch cap in the separated state of the present invention;

Fig. 5 is a structural schematic diagram of the supporting ring of the present invention;

Fig. 6 is a schematic diagram of the angle of the cam working surface of the present invention.

detailed description

Below in conjunction with accompanying drawing and specific embodiment the present invention is described in further detail:

As shown in Figure 1, it is a schematic diagram of the installation structure of the clutch body and the clutch cap of the present invention. The split type springless overrunning clutch of the present invention includes a clutch body 1 and a clutch cap 5, wherein the clutch body 1 is installed on the hydraulic motor shaft 3, and passes through the shaft shoulder. To achieve axial positioning, it is fixed in the axial direction by the elastic circlip 4, and is transmitted by two flat keys 2 symmetrically arranged along the circumferential direction; the clutch cap 5 is installed on the motor shaft 6 through the spline, and the axial positioning is performed by the washer 7 , fixed axially by the circlip 8 .

As shown in Figure 2, it is a schematic structural view of the clutch main body of the present invention, wherein Figure 2a is a front view of the clutch main body, Figure 2b is a sectional view along A-A, and Figure 2c is a sectional view along B-B; as can be seen from the figure, the clutch main body 1 is composed of a cam 11 , support ring 12, rivet 13, rolling bar 14 and cover plate 15, and rolling bar 14 is N, and as shown in Figure 5 is the schematic diagram of the support ring structure of the present invention, and support ring 12 is a ring structure, and on the edge of the ring structure Evenly distributed N blind holes 12-1 are used to place N rolling bars 14. The bottom of the ring structure is a stepped hole, and the cam 11 is placed in the stepped hole and supported by the step 12-2, wherein the blind hole 12 The bottom of -1 and the bottom of step 12-2 can be on the same plane. The cover plate 15 encapsulates the cam 11 and the rolling rod 14 inside the support ring 12 , and the cover plate 15 and the edge of the support ring 12 are fixedly connected by rivets 13 .

The cam 11 has a circular structure, and N working areas and N non-working areas 21 are alternately distributed on the outer surface of the circular structure. 12, the inner surface of the edge is matched, and each working area includes an engagement area 16 and a separation area 17, and the engagement area 16 and the separation area 17 are connected by a transition slope 20, and the rolling rod 14 is in contact with the engagement area 16 to realize the clutch body 1 and the clutch cap. 5, the roller bar 14 is in contact with the separation zone 17 to realize the separation of the clutch body 1 and the clutch cap 5, wherein N is a positive integer, and N≥3.

Wherein the engagement area 16 and the separation area 17 are both planes, and the two planes of the engagement area 16 and the separation area 17 are parallel. The included angle between the transition slope 20 and the plane of the separation zone 17 (or the plane of the meshing zone 16 ) is 120°-150°, preferably 130°-140°.

As shown in Fig. 6 , the angle diagram of the cam face of the present invention is shown. The ratio of the wrap angle α of the meshing zone 16 to the center of the circle and the wrap angle β of the separation zone 17 to the circle center satisfies: α:β=0.7～0.9:1. The ratio of the wrap angle δ of each non-working area to the center of the circle and the wrap angle α of the meshing area 16 to the center of the circle satisfies: δ:α=0.8˜0.9:1.

As shown in Figure 3, it is a schematic diagram of the relative position of the clutch body of the present invention and the clutch cap in the engaged state, and Figure 4 is a schematic diagram of the relative position of the clutch body of the present invention and the clutch cap in the separated state, and the main working principle of the overrunning clutch of the present invention is as follows :

The working principle of the engagement of the clutch body 1 and the clutch cap 5 is (as shown in Figure 3):

1) In the initial state, the cam 11, the roller 14 and the support ring 12 are relatively stationary;

2) At the moment when the hydraulic motor shaft 3 is started, the cam 11 rotates clockwise accordingly. At this time, the support ring 12 and the rolling rod 14 remain still. The ring 12 is constrained, jumps from the plane of the separation area 17 of the cam 11 to the plane of the higher engagement area 16, contacts with the clutch cap 5 and enters into engagement;

3) The clutch body 1 is engaged with the clutch cap 5 to form a synchronously rotating torque transmission assembly.

The working principle of the disengagement of the clutch body 1 from the clutch cap 5 is (as shown in Figure 4):

When the clutch cap 5 rotates relatively fast relative to the clutch main body 1, under the action of friction, the clutch cap 5 drives the roller bar 14 to fall from the plane of the engagement area 16 of the cam 11 to the plane of the lower disengagement area 17, and the roller bar 14 is in contact with the clutch. The cap 5 is out of contact, and the clutch body 1 and the clutch cap 5 are no longer engaged.

The main body 1 of the clutch of the present invention adopts a springless structure, and relies on the relative movement between the cam 11 and the support ring 12 and the roller 14 to realize the engagement and disengagement with the clutch cap. The power transmission route in the meshing state is as follows: in the hydraulic motor drive mode, the power is output by the shaft 3 of the hydraulic motor, passed to the cam 11 through two flat keys 2, and then transferred to the clutch cap 5 through the roller rod 14, and then passed through the spline Connect the shaft 6 that passes to the motor. Drive the motor shaft and the plunger pump coaxially connected with it to rotate; in the motor driving mode, the hydraulic motor shaft does not rotate, and the clutch cap 5 is automatically disengaged from the clutch main body 1 . The adoption of the springless structure enables automatic engagement and disengagement by mechanical movement, which has higher reliability than the spring-structured overrunning clutch.

The split structure is adopted, the clutch main body 1 and the clutch cap 5 are respectively arranged on the active element hydraulic motor and the driven element electric motor, and the two elements are produced and managed separately, without separate installation and combination, and are automatically installed in place with the installation of the two elements . Easy to disassemble, use and manage.

The split-type springless overrunning clutch involved in the present invention is mainly used in the hydraulic servo system of a new generation of launch vehicles, and is the transmission/control element of the hydraulic servo system. It has the functional characteristics of "one-way meshing/transmission, reverse disengagement", To adapt to the autonomous switching of the sky/ground drive mode of the servo mechanism.

Example 1

As shown in Figure 2, the support ring 12 in this embodiment includes a central stepped hole and six blind holes, the cam 11 is located in the central stepped hole of the support ring 12, and is supported by the steps, and the six rolling rods 14 are respectively located in the support ring. 12 in the six blind holes; then the cam 11 and the rolling rod 14 are packaged inside the support ring 12 through the cover plate 15, and the cover plate 15 and the support ring 12 are connected by rivets 13, the cam 11, the support ring 12, The rivet 13, the rolling rod 14 and the cover plate 15 jointly form the clutch main body 1.

As shown in Figure 6, in this embodiment, there are six working areas and non-working areas, which are evenly distributed on the circumference of the cam 11. The six working areas have the same structural shape, and the six non-working areas 21 are also in the same structural shape. of six arcs. The wrap angle δ of each non-working area 21 to the center of the circle is 13-16°, the wrap angle α of the 16 pairs of circle centers in the meshing area is 17-19°, and the wrap angle β of the 17 pairs of circle centers in the separation area is 22-24° , The wrapping angle γ of the transition zone between the meshing zone 16 and the separation zone 17 to the center of the circle is 1-3°.

The clutch body 1 and the clutch cap 5 are made of steel.

The above description is only the best specific implementation mode of the present invention, but the protection scope of the present invention is not limited thereto. Any skilled person familiar with the technical field can easily think of changes and changes within the technical scope disclosed in the present invention. Replacement should be covered within the protection scope of the present invention.

Parts not described in detail in the present invention belong to the common knowledge of those skilled in the art.

Claims (10)

1. a kind of split type no spring freewheel clutch it is characterised in that：Including clutch main body (1) and clutch cap (5), wherein Clutch main body (1) is fixedly mounted on the arbor that surges (3), and with the arbor that surges (3) synchronous axial system, the fixing peace of clutch cap (5) It is contained on motor reel (6), and and motor reel (6) synchronous axial system；Described clutch main body (1) includes cam (11), backing ring (12) and N number of roller (14), its cam (11) is located at the middle part of backing ring (12), and it is outside that N number of roller (14) is located at cam (11), It is uniformly distributed along backing ring (12) edge, described cam (11) is circular configuration, and circular configuration outer surface is alternately distributed N number of work Area and N number of nonclient area (21), the outer surface of each nonclient area (21) is coordinated with the inner surface at backing ring (12) edge, each work Include region of engagement (16) and Disengagement zone (17) as area, pass through intermediate incline (20) between region of engagement (16) and Disengagement zone (17) even Connect, roller (14) is contacted with region of engagement (16) realizes engaging of clutch main body (1) and clutch cap (5), roller (14) with separate Area (17) contact is realized clutch main body (1) and is separated with clutch cap (5), and wherein N is positive integer, and N >=3.

2. one kind split type no spring freewheel clutch according to claim 1 it is characterised in that：Described region of engagement (16) It is plane with Disengagement zone (17).

3. one kind split type no spring freewheel clutch according to claim 2 it is characterised in that：Described region of engagement (16) Parallel with two planes of Disengagement zone (17).

4. the split type no spring freewheel clutch of the one kind according to one of claims 1 to 3 it is characterised in that：Described mistake Crossing the angle between inclined-plane (20) and Disengagement zone (17) plane is 120 °～150 °.

5. one kind split type no spring freewheel clutch according to claim 4 it is characterised in that：Described intermediate incline (20) angle and Disengagement zone (17) plane between is 130 °～140 °.

6. one kind split type no spring freewheel clutch according to claim 1 it is characterised in that：Described backing ring (12) is Circular ring structure, circular ring structure edge is uniformly distributed N number of blind hole (12-1), for placing N number of roller (14), circular ring structure bottom For stepped hole, cam (11) is placed in described stepped hole, and is supported by step (12-2).

7. the split type no spring freewheel clutch of the one kind according to claim 1 or 6 it is characterised in that：Described clutch Main body (1) also includes cover plate (15) and rivet (13), and cam (11) and roller (14) are encapsulated in backing ring by its cover plate (15) (12) internal, cover plate (15) is fixedly connected by rivet (13) with backing ring (12) edge.

8. the split type no spring freewheel clutch of the one kind according to one of claims 1 to 3 it is characterised in that：Described nibble Closing area (16) to the wrap angle sigma in the center of circle and the ratio of the cornerite β to the center of circle for the Disengagement zone (17) is satisfaction：α:β=0.7～0.9:1.

9. the split type no spring freewheel clutch of the one kind according to one of claims 1 to 3 it is characterised in that：Described every The circular arc of individual nonclient area is met with the ratio of the wrap angle sigma to the center of circle for the region of engagement (16) to the cornerite δ in the center of circle：δ:α=0.8～ 0.9:1.

10. the split type no spring freewheel clutch of the one kind according to one of claims 1 to 3 it is characterised in that：Described from Clutch main body (1) is arranged on the arbor that surges (3), realizes axially position by the shaft shoulder, solid vertically by circlip (4) Fixed, it is driven by two flat keys (2) being along the circumferential direction arranged symmetrically；Clutch cap (5) is arranged on motor by spline On axle (6), axially position is carried out by packing ring (7), be axially fixed by circlip (8).