Overload protection coupling

Abstract

The utility model relates to an overload protection coupler, which comprises a half coupler and a shell, an annular gland and an end cover are respectively arranged at two ends of the shell, the outer side of the end cover is connected with the half coupler, the inner side of the end cover is fixedly connected with a bearing seat, a connecting shaft sleeve is arranged between the bearing seat and the annular gland, and a spring is sleeved between the bearing seat and the connecting shaft sleeve. A plurality of first friction plates are slidably arranged on the connecting shaft sleeve between the spring and the annular gland in a sleeving mode, a first protruding block is fixedly connected to the outer ring of each first friction plate, the first friction plates are slidably connected with the shell through the first protruding blocks, and a second friction plate arranged on the connecting shaft sleeve in a sleeving mode is further arranged between every two adjacent first friction plates; the inner ring of each second friction plate is fixedly connected with a second protruding block and is in sliding connection with the connecting shaft sleeve through the second protruding block, the annular gland is in threaded connection with the shell, the coupler has the overload protection function, the coupler and all components connected with the coupler can be prevented from being damaged, and the compression degree of the spring can be conveniently adjusted.

Description

Technical Field

[0001] The utility model belongs to the technical field of couplings, in particular to an overload protection coupling. Background Art

[0002] A coupling is a connecting piece used to connect the driving shaft and the driven shaft, and is used to achieve synchronous rotation between the driven shaft and the driving shaft. For existing rigid couplings, during use, when the load on the driven shaft is too large and exceeds the torque that the coupling itself can withstand, the coupling and the components connected to the coupling will be damaged. Therefore, there are overload protection couplings on the market.

[0003] For example, the utility model patent with the announcement number CN205533878U in the existing patents discloses an overload protection coupling for a press. When in use, the patent can adjust the compression amount of the spring member through the nut at the right end of the bolt, change the positive pressure on the friction block, and change the friction force transmitted by the friction block. However, when adjusting the positive pressure on the friction block, the above patent needs to adjust the position of each nut separately, which is more troublesome; in addition, after adjusting the position of the nut, the compression degree of each spring member sometimes cannot be kept consistent, which is not convenient for adjustment operation. Therefore, there are still shortcomings and deficiencies in the prior art. Utility Model Content

[0004] The purpose of the utility model is to provide an overload protection coupling to solve the problems raised in the above background technology.

[0005] In order to solve the above problems, the technical solution adopted by the utility model is:

[0006] An overload protection coupling comprises a half coupling and a shell, wherein the shell is a tubular structure with two ends open, and an annular gland and an end cap are respectively installed at the two ends of the shell, the outer side of the end cap is connected to the half coupling, the inner side of the end cap is coaxially fixedly connected to a bearing seat, a connecting sleeve coaxially arranged with the annular gland and rotatable is arranged between the bearing seat and the annular gland, and a spring in a compressed state is jointly sleeved between the bearing seat and the connecting sleeve, and a plurality of first friction sleeves are provided on the sliding sleeve of the connecting sleeve between the spring and the annular gland The outer ring of each first friction plate is fixed with a first protrusion and is slidably connected to the outer shell along the axial direction of the outer shell through the first protrusion, and the first friction plate arranged close to the spring abuts against the spring, and the first friction plate arranged close to the annular pressure cover abuts against the annular pressure cover, and a second friction plate sleeved on the connecting shaft sleeve is also arranged between every two adjacent first friction plates, and the second friction plates abut against the first friction plates respectively, and the inner ring of each second friction plate is fixed with a second protrusion and is slidably connected to the connecting shaft sleeve along the axial direction of the connecting shaft sleeve through the second protrusion.

[0007] Furthermore, a retaining ring is coaxially fixedly mounted on the bearing seat, the spring is in contact with the retaining ring, and the annular gland is threadedly connected to the outer shell.

[0008] Furthermore, both sides of the inner wall of the shell are provided with first slide grooves arranged parallel to the shell, the number of the first protrusions is two, each of the first protrusions is respectively located in the first slide groove and is slidably connected to the shell through the first slide groove, and both sides of the outer wall of the connecting sleeve are provided with second slide grooves arranged parallel to the connecting sleeve, the number of the second protrusions is two, each of the second protrusions is respectively located in the second slide groove and is slidably connected to the connecting sleeve through the second slide groove.

[0009] Furthermore, the first slide groove is of equal length to the outer shell, and an end of the second slide groove away from the end cover is flush with the end of the outer shell.

[0010] Furthermore, the outer circumference of the annular pressure cover is provided with a plurality of notches equidistantly distributed along the circumference of the annular pressure cover, and the outer wall of the outer shell at one end away from the half-coupling is provided with an annular groove, and a matching locking steel wire is arranged in the annular groove, and one end of the locking steel wire passes through the outer shell along the radial direction of the outer shell and is located in one of the notches.

[0011] Furthermore, the half coupling includes a connecting tube, one end of which is fixedly mounted with a connecting disk, the connecting disk and the end cover are connected via a plurality of elastic pins equidistantly distributed along the circumference of the connecting disk, and the elastic pins are arranged parallel to the connecting tube.

[0012] Furthermore, a receiving groove is coaxially arranged at one end of the bearing seat away from the end cover, and a limiting shaft sleeve is fixed in the receiving groove.

[0013] Furthermore, the radial cross-section of the shell is annular.

[0014] By adopting the above technical solution, the beneficial effects of the utility model are:

[0015] When the utility model is in use, the half coupling can be sleeved on the driving shaft and fixed in position with the driving shaft, and the connecting sleeve can be sleeved on the driven shaft and fixed in position with the driven shaft. Then, when the load on the driven shaft is not overloaded, under the action of the spring and the annular pressure cover jointly squeezing the first friction plate and the second friction plate, the first friction plate and the second friction plate are statically frictioned against each other, that is, the first friction plate and the second friction plate are relatively stationary. At this time, under the cooperation of the first protrusion and the second protrusion, the connecting sleeve can be synchronously rotated with the half coupling through the housing to realize synchronous rotation of the driven shaft and the driving shaft. When the load on the driven shaft is overloaded, that is, when the load torque is greater than the maximum static friction force between the first friction plate and the second friction plate, When the static friction between the first friction plate and the second friction plate switches to dynamic friction, slipping occurs. At this time, the connecting sleeve may not rotate with the rotation of the half coupling, thereby protecting the coupling to prevent damage to the coupling and the components connected to the coupling. In general, the utility model is a coupling with an overload protection function, which can avoid damage to the coupling and the components connected to the coupling under overload conditions; secondly, since the annular pressure cover is threadedly connected to the outer shell, when in use, the first friction plate and the second friction plate can be slid in the outer shell by rotating the annular pressure cover to adjust the compression degree of the spring. Compared with the prior art, the above adjustment method can facilitate the adjustment of the compression degree of the spring. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 It is a structural schematic diagram of the utility model;

[0017] Figure 2 This is one of the structural schematic diagrams of the utility model in a split state of a part of the device;

[0018] Figure 3 This is the second structural diagram of the utility model in which part of the device is in a split state;

[0019] Figure 4 It is a schematic diagram of the structure of part of the device of the utility model in a cross-sectional state.

[0020] Figure numerals: 1. first friction plate; 2. second friction plate; 3. spring; 4. housing; 41. first slide groove; 42. annular groove; 43. through hole; 5. half coupling; 51. connecting pipe; 52. connecting plate; 6. annular pressure cover; 61. notch; 7. end cover; 8. bearing seat; 9. connecting sleeve; 91. second slide groove; 10. first protrusion; 11. second protrusion; 12. retaining ring; 13. locking wire; 14. limiting sleeve; 15. rubber ring; 16. pin; 17. locking nut; 18. retaining ring. DETAILED DESCRIPTION

[0021] In order to make the purpose, technical solution and beneficial effects of the present invention clearer, the implementation mode of the present invention is further described in detail below with reference to the accompanying drawings.

[0022] like Figures 1 to 4 As shown, the utility model provides an overload protection coupling, including a half-coupling 5. Specifically, the half-coupling 5 is a prior art. When in use, the half-coupling 5 is sleeved on the driving shaft and fixed in position to the driving shaft; the utility model also includes a shell 4, which is a tubular structure with openings at both ends, and an annular gland 6 and an end cover 7 are respectively installed at both ends of the shell 4, and the outer side of the end cover 7 is connected to the half-coupling 5, that is, the shell 4 can rotate synchronously with the half-coupling 5; a bearing seat 8 is coaxially fixedly connected to the inner side of the end cover 7, and a connecting sleeve 9 which is coaxially arranged with the annular gland 6 and can rotate is arranged between the bearing seat 8 and the annular gland 6. Specifically, when in use, the driven shaft can be inserted into the connecting sleeve 9 after passing through the annular gland 6, and then the driven shaft and the connecting sleeve 9 are fixed in position by a connecting key; and a spring 3 in a compressed state is jointly sleeved between the bearing seat 8 and the connecting sleeve 9, and is located between the spring 3 and the annular gland 6 A plurality of first friction plates 1 are provided on the sliding sleeve of the connecting sleeve 9 between the two members, and the first friction plates 1 are annular; the outer ring of each first friction plate 1 is fixedly connected with a first protrusion 10 and is slidably connected with the outer shell 4 along the axial direction of the outer shell 4 through the first protrusion 10, that is, under the action of the first protrusion 10, the first friction plate 1 can rotate synchronously with the outer shell 4; and the first friction plate 1 arranged close to the spring 3 abuts against the spring 3, and the first friction plate 1 arranged close to the annular pressure cover 6 abuts against the annular pressure cover 6, and a second friction plate 2 sleeved on the connecting sleeve 9 is also provided between every two adjacent first friction plates 1, and the second friction plate 2 is annular; the second friction plates 2 abut against the first friction plates 1 respectively, and the inner ring of each second friction plate 2 is fixedly connected with a second protrusion 11 and is slidably connected with the connecting sleeve 9 along the axial direction of the connecting sleeve 9 through the second protrusion 11, and under the action of the second protrusion 11, the second friction plate 2 can rotate synchronously with the connecting sleeve 9.

[0023] Specifically, when in use, when the load on the driven shaft is not overloaded, under the action of the spring 3 and the annular pressure cover 6 jointly squeezing the first friction plate 1 and the second friction plate 2, the first friction plate 1 and the second friction plate 2 are statically frictioned against each other, that is, the first friction plate 1 and the second friction plate 2 are relatively stationary. At this time, the connecting sleeve 9 can be synchronously rotated with the half coupling 5 through the housing 4 under the cooperation of the first protrusion 10 and the second protrusion 11, so as to realize the synchronous rotation of the driven shaft and the driving shaft; when the load on the driven shaft is overloaded, that is, when the load torque is large, When the static friction force between the first friction plate 1 and the second friction plate 2 is at its maximum, the static friction between the first friction plate 1 and the second friction plate 2 switches to dynamic friction and slipping occurs. At this time, the connecting sleeve 9 may not rotate with the rotation of the half-coupling 5, thereby protecting the coupling to prevent damage to the coupling and the components connected to the coupling. In general, the utility model is a coupling with an overload protection function, which can prevent damage to the coupling and the components connected to the coupling, such as a motor, a reducer, etc., under an overload state.

[0024] Secondly, the annular pressure cover 6 is threadedly connected to the outer shell 4. Specifically, an internal thread is provided in the outer shell 4, and an external thread is provided on the annular pressure cover 6, so that the annular pressure cover 6 can be easily disassembled and assembled on the outer shell 4; in addition, by rotating the annular pressure cover 6, the first friction plate 1 and the second friction plate 2 can be slid in the outer shell 4 to adjust the compression degree of the spring 3, thereby adjusting the maximum static friction force between the first friction plate 1 and the second friction plate 2, which is suitable for different working occasions; and compared with the prior art, the above-mentioned adjustment method can facilitate the adjustment of the compression degree of the spring 3.

[0025] The specific configuration of the first friction plate 1 being slidably connected to the housing 4 via the first protrusion 10 is as follows: Figure 3 As shown, first slide grooves 41 arranged parallel to the shell 4 are provided on both sides of the inner wall of the shell 4, and the number of first protrusions 10 is two, each of which is located in the first slide grooves 41 and is slidably connected with the shell 4 through the first slide grooves 41, so that the stability of the first friction plate 1 during the sliding process can be improved, and under the action of the first protrusions 10, the first friction plate 1 can be synchronously rotated with the shell 4; the specific setting method of the second friction plate 2 being slidably connected with the connecting sleeve 9 through the second protrusions 11 is as follows: Figure 2 As shown, second sliding grooves 91 parallel to the connecting sleeve 9 are provided on both sides of the outer wall of the connecting sleeve 9, and the number of second protrusions 11 is two. Each second protrusion 11 is located in the second sliding groove 91 and is slidably connected to the connecting sleeve 9 through the second sliding groove 91. This can improve the stability of the second friction plate 2 during the sliding process, and under the action of the second protrusion 11, the second friction plate 2 and the connecting sleeve 9 can rotate synchronously.

[0026] Further, such as Figure 2and Figure 3 As shown, the first slide groove 41 is of the same length as the outer shell 4, and the end of the second slide groove 91 away from the end cover 7 is flush with the end of the outer shell 4, so that after removing the annular pressure cover 6, the first friction plate 1, the second friction plate 2 and the spring 3 can be easily disassembled and assembled in the outer shell 4, thereby facilitating the replacement of the first friction plate 1, the second friction plate 2 and the spring 3.

[0027] Further, such as Figure 1 , Figure 3 and Figure 4 As shown, the outer circumference of the annular gland 6 is provided with a plurality of notches 61 equidistantly distributed along the circumference of the annular gland 6, and the notches 61 penetrate the annular gland 6 along the axial direction of the annular gland 6; an annular groove 42 is provided on the outer wall of the end of the housing 4 away from the half-coupling 5, and a matching locking wire 13 is arranged in the annular groove 42, and the locking wire 13 is removable; one end of the locking wire 13 passes through the housing 4 along the radial direction of the housing 4 and is located in one of the notches 61, specifically, the locking wire 13 penetrates the housing 4 through the through hole 43 opened along the radial direction of the housing 4; and by providing the locking wire 13, the annular gland 6 cannot be easily rotated, thereby assisting in fixing the position of the annular gland 6 on the housing 4; then when the annular gland 6 needs to be rotated, the locking wire 13 can be pulled out from the notch 61, and then the annular gland 6 is rotated, and when the through hole 43 is relative to one of the notches 61 again, the locking wire 13 can be reinserted into the notch 61.

[0028] Further, such as Figure 1 As shown, the half coupling 5 includes a connecting tube 51. Specifically, a screw penetrating the connecting tube 51 is connected along the radial thread of the connecting tube 51. When in use, the half coupling 5 can be fixed to the driving shaft by the screw; one end of the connecting tube 51 is fixedly sleeved with a connecting plate 52, and the connecting plate 52 is connected to the end cover 7 by a plurality of elastic pins equidistantly distributed along the circumference of the connecting plate 52. The elastic pins are arranged in parallel with the connecting tube 51. Specifically, the arrangement method of the elastic pins refers to the structure of the elastic pin coupling in the prior art; that is, the elastic pins It includes a pin 16 with a head. When installed, the head of the pin 16 is located in the housing 4, and the pin 16 passes through the end cover 7 and the connecting plate 52 in sequence and is then fitted with a locking nut 17. A retaining ring 18 and a rubber ring 15 are also fitted on the pin 16 between the head of the pin 16 and the end cover 7 in sequence. In this way, when the locking nut 17 is pressed against the connecting plate 52, the half coupling 5 can be easily installed on the end cover 7. When in use, since the rubber ring 15 can be deformed, the half coupling 5 can move axially within a certain range for easy use.

[0029] In addition, a retaining ring 12 is coaxially fixedly mounted on the bearing seat 8, and the spring 3 is in contact with the retaining ring 12, that is, under the cooperation of the retaining ring 12 and the first friction plate 1, the spring 3 can be in a compressed state; in addition, as Figure 1 As shown, the rubber ring 15 arranged close to the retaining ring 12 is located on the side of the retaining ring 12 away from the spring 3, that is, the elastic pin and the spring 3 do not interfere with each other.

[0030] Furthermore, a receiving groove is coaxially provided on one end of the bearing seat 8 away from the end cover 7, and a limiting sleeve 14 is fixed in the receiving groove. Specifically, when in use, the driven shaft can be passed through the annular pressure cover 6 and the connecting sleeve 9 in sequence, and then inserted into the limiting sleeve 14, so that the connecting sleeve 9 can be limited along the radial direction of the connecting sleeve 9 to prevent the connecting sleeve 9 from radial displacement.

[0031] Furthermore, the radial cross section of the housing 4 is annular, so when in use, a brake can be provided to brake the housing 4, that is, the housing 4 can be used as a brake wheel, so that the utility model has a braking function.

[0032] The above shows and describes the basic principle, main features and advantages of the utility model. Those skilled in the art should understand that the utility model is not limited by the above embodiments. The above embodiments and descriptions are only for explaining the principle of the utility model. The utility model may have various changes and improvements without departing from the spirit and scope of the utility model. These changes and improvements fall within the scope of the utility model to be protected. The scope of protection claimed by the utility model is defined by the attached claims and their equivalents.

Claims

1. An overload protection coupling, comprising a half coupling, characterized in that: It also includes an outer shell, which is a tubular structure with openings at both ends, and an annular pressure cover and an end cover are respectively installed at both ends of the outer shell, the outer side of the end cover is connected to the half coupling, and the inner side of the end cover is coaxially fixedly connected to a bearing seat, a connecting sleeve coaxially arranged with the annular pressure cover and rotatable is arranged between the bearing seat and the annular pressure cover, and a spring in a compressed state is jointly sleeved between the bearing seat and the connecting sleeve, and a plurality of first friction plates are slidingly sleeved on the connecting sleeve between the spring and the annular pressure cover, the outer ring of each first friction plate is fixedly connected to a first protrusion and is slidably connected to the outer shell along the axial direction of the outer shell through the first protrusion, and the first friction plate arranged close to the spring abuts against the spring, and the first friction plate arranged close to the annular pressure cover abuts against the annular pressure cover, and a second friction plate sleeved on the connecting sleeve is also arranged between every two adjacent first friction plates, the second friction plates respectively abut against the first friction plates, and the inner ring of each second friction plate is fixedly connected to a second protrusion and is slidably connected to the connecting sleeve along the axial direction of the connecting sleeve through the second protrusion, and the annular pressure cover is threadedly connected to the outer shell.

2. An overload protection coupling according to claim 1, characterized in that: Both sides of the inner wall of the shell are provided with first slide grooves arranged parallel to the shell, the number of the first protrusions is two, each of the first protrusions is respectively located in the first slide groove and is slidably connected to the shell through the first slide groove, and both sides of the outer wall of the connecting sleeve are provided with second slide grooves arranged parallel to the connecting sleeve, the number of the second protrusions is two, each of the second protrusions is respectively located in the second slide groove and is slidably connected to the connecting sleeve through the second slide groove.

3. An overload protection coupling according to claim 2, characterized in that: The first slide groove is as long as the shell, and one end of the second slide groove away from the end cover is flush with the end of the shell.

4. The overload protection coupling according to claim 1, characterized in that: The outer circumference of the annular gland is provided with a plurality of notches equidistantly distributed along the circumference of the annular gland, and the outer wall of the shell at one end away from the half-coupling is provided with an annular groove, in which a matching locking steel wire is arranged, and one end of the locking steel wire passes through the shell in the radial direction of the shell and is located in one of the notches.

5. The overload protection coupling according to claim 1, characterized in that: The half coupling comprises a connecting tube, one end of which is fixedly sleeved with a connecting disk, the connecting disk and the end cover are connected by a plurality of elastic pins equidistantly distributed along the circumference of the connecting disk, and the elastic pins are arranged parallel to the connecting tube.

6. The overload protection coupling according to claim 1, characterized in that: An accommodating groove is coaxially arranged at one end of the bearing seat away from the end cover, and a limiting shaft sleeve is fixedly installed in the accommodating groove.

7. The overload protection coupling according to claim 1, characterized in that: The radial cross section of the shell is annular.

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