Cam clamp with a swinging clamp arm

Abstract: A cam clamp (10) includes a swing clamp arm (32) and multiple options for driving the clamp (10). The movement of a locking cam (14) within a clamp header (16) influences a central shaft (12) having a clamp member (32) attached thereto to rotate from a first rest position to a second clamping position, then causes the central shaft (12)(with the clamp member (32) mounted thereon) to move axially downwards to exert a clamping force. In a second embodiment, the rotational movement of a locking ring (114) causes a central shaft (112), having a clamp member (132) attached thereto, to rotate with it from a first rest position to a second clamping position. At the second position, the shaft (112) is restrained from further rotation, but the locking ring (114) continues as before. An appropriately inclined upper surface (114a) of the locking ring (114) comes into sliding contact beneath the clamp member (132), causing the clamp member (132) to pivot downwards with steadily increasing clamping force.

Description: The present invention relates to a cam clamp according to the preamble of claim 1, and in particular to such clamping devices provided with a swinging clamp arm which moves from a first release position to a second position where the clamp is actuated to clamp a desired object. Description of Related Art: Several types of clamps for clamping objects such as dies, fixtures, molds, and parts in machining operations are known. Such devices generally use hydraulic power to exert clamping force, but require continuous pressure application to maintain clamping. Some devices, like that disclosed in U.S. Patent No. 4,721,293, teach the use of a hydraulic mechanism to close the clamp initially, but then uses a self-locking mechanism to eliminate the need for continued hydraulic pressure. JP 56-39846 also uses hydraulic power in combination with a mechanical lock. However, these clamping devices must be located or positioned manually, or by an auxiliary system, thereby increasing their operational change-over time and their cost of manufacture. To eliminate such inefficiencies, swing clamps with a cam sleeve and/or a cam slot operated pneumatically, hydraulically, or manually are known, such as in U.S. Patent No. 5,013,015. However, these devices do not exert locking forces as strong as those described above. However, those described previously do not present the benefit of a swinging clamp arm. A device that provides a swing clamp arm and a strong locking force is disclosed in U.S. Patent No. 4,830,349. However, it represents a relatively expensive concept and requires continuous pressure from a hydraulic pump for operation, resulting in additional operating costs from continuous operation and maintenance. A cam clamp according to the preamble of claim 1 is disclosed in DE-A-36 03 618. Here, the central shaft is in the form of a thread bolt and the central shaft is actuated by a pinion which is threaded on the thread bolt and which is rotatably arranged in the housing of the clamping device. The pinon 9 is actuated by a further pinion 17 also rotatably arranged in the housing. By rotating the pinion 9 via the pinion 17, the shaft 6 together with the clamp member 5 is first rotated and then axially moved into a clamping position. It is an object of the present invention to provide a cam clamp which is advantageously simple, reliable, and efficient in operation, and is inexpensive and easy to manufacture. This object is solved by a cam clamp as defined in claim 1. The subclaims concern particular embodiments of the invention. The present invention provides a mechanical clamp with a swinging clamp arm with strong clamping action and without the need for continuous pressure application while clamping is performed. In addition, such clamping can be activated and deactivated with different driving options, including, but not limited to manual, pneumatic, or hydraulic operation. Each option has operational advantages associated therewith. The present invention provides a clamp with a swing clamp member which is mounted on a rotatable central shaft within a clamp header. A locking cam with an engaging member, such as a pin member, is also provided within the header, substantially perpendicular to the central shaft. The locking cam has at least one surface which is at least partially inclined. The locking cam can also move in a line within its plane. When the locking cam is moved relative to the central shaft in operation, the engaging member engages the shaft, in a groove provided in the shaft, for example. The continued motion of the locking cam causes the shaft, with the clamp member attached, to rotate from a first position to a second position. At the second position, the engaging member disengages from the shaft, thus stopping the further rotation of the shaft (and the clamp member). The locking cam continues to move in the same direction beneath and in sliding contact with the shaft, however, and its inclined surface causes the shaft to cause the clamp member to pivot downwards to exert a clamping force as desired. The locking cam is moved in the opposite direction to reverse the process for unclamping an object. The movement of the locking cam is achieved by an auxiliary driving source connected thereto, which can include pneumatic or hydraulic cylinders, mechanical power sources, or manual actuation. Other objects, features, and characteristics of the present invention, as well as methods of operation and function of the related elements of structure, and the combination of parts and economies of manufacture, will become more apparent upon consideration of the following detailed description and the appended claims with reference to the accompanying drawings, all of which form a part of this specification. BRIEF DESCRIPTION OF THE DRAWINGS Figures 1 through 5 illustrate a first embodiment of the present invention. Figures 6 and 7 illustrate additional alternative embodiments. It is emphasized that these embodiments are illustrative and should not be construed as limiting the scope of the invention. Figure 1 is a plan view of the invention, partially in section, according to a first embodiment, taken along line 1-1 of Figure 2. Figure 2 is a sectional view taken along line 2-2 of Figure 1. Figure 3 is a sectional view taken along line 3-3 of Figure 1. Figure 4 is sectional view along line 4-4 of Figure 3. Figure 5 is a plan view of the invention according to the first embodiment of the invention showing one possible auxiliary drive source. Figure 6 is a plan view of an alternative embodiment of the invention, partially in section and including dual clamp assemblies using as auxiliary drive sources pressurizable cylinders operable from the same pressure source. Figure 7 is a side elevation of another alternative embodiment of the present invention, which clamps with even greater pressure. DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS In the following detailed description of preferred embodiments, like features of the different embodiments will carry the same reference numeral except for a different prefix number common to a particular example. Figures 1 through 5 illustrate the present invention, according to a first embodiment. Cam clamp 10 includes a central shaft 12 which is rotatably disposed within clamp header 16. Clamp header 16 is in turn mounted on base 18. Shaft 12 has an opposite cam 20 mounted at one axial end thereof by nut 28 and lock pin 62. A clamp member 32 is mounted at the opposite end of shaft 12, for example by a pin 34. A locking cam 14 is also disposed within clamp header 16 in a plane substantially perpendicular to the longitudinal axis of the central shaft 12. Locking cam 14 has an inclined surface in sliding contact with the opposite cam 20 and is moveable within its plane. The locking cam 14 also includes an engaging member, such as a pin member 22 as illustrated. In operation, locking cam 14 is made to move by an auxiliary driving source, described below. Through the movement of locking cam 14, the engaging pin 22 is moved to a position where it engages a portion of the central shaft 12. This causes shaft 12 and clamp member 32 attached thereto to rotate away from a first position. The central shaft 12 may be provided with a suitably placed notch or groove structure 12a to receive the engaging member 22 to facilitate engagement therebetween, for example. After a certain rotational distance, the engaging member 22 disengages from the central shaft 12, due to the nature of its line of travel relative to the shaft. Simultaneously, a stop member, such as a' stop pin 24, is optionally provided which also acts to prevent further rotation of the central shaft 12. The resultant effect stops the central shaft 12 and clamp member 32 at a second position, shown in phantom in Figure 4. This second position corresponds to the position where clamping is intended to take place. After the engaging pin 22 disengages from the central shaft, the locking cam 14 on which the engaging pin 22 is mounted continues to move in the same direction, under the influence of the auxiliary driving source. Hereafter, an inclined portion 14A of locking cam 14 comes into sliding contact with the opposite cam 20. The downward, wedge-like action of the inclined portion 14A against opposite cam 20 causes the nut 28, which is attached to the opposite cam 20, to move axially downwards. Because the nut 28 is attached to the central shaft 12, it in turn causes clamp member 32, mounted at the other end of shaft 12, to likewise move in the same downward direction and exert a clamping force to clamp work piece 40 onto a work bench 42 as desired. Clamp release is achieved by simply reversing the process ( i.e. , by the reverse movement of the locking cam 14), whereby the clamping force is removed and the clamp member 32 is rotated by the central shaft 12 back to the first release position. The invention according to this embodiment is operated by an auxiliary drive source of any of several types, including, but not limited to, pneumatic or hydraulic cylinders, mechanical power sources, or manual actuation. Each has operational advantages associated with it. For example, manual actuation eliminates the need for connection to an external power source. Pressurized cylinders or a mechanical source allow for automated and/or remote operation of the clamp. In the first embodiment as shown in Figures 1 and 2, a pressurized piston cylinder 48 is used as an example. The base 46 of cylinder 48 is connected with the clamp 10. In operation, in general, the piston 52 is connected by cylinder shaft 26 to the locking cam 14. Thus, when cylinder 48 is pressurized and de-pressurized, it causes piston 52 to move locking cam 14 with shaft 26, as described above. However, for added safety, the clamping action can be achieved by using a steel or gas spring action 60, which assuredly tends to act in a direction to accomplish clamping ( i.e. , clamp closure). The auxiliary drive source is then used only for the unclamping action. This arrangement helps to prevent accidental loss of clamping force due to physical separation of pressure lines or loss of pressure therein. Locking spring action 162, seen in Figure 12, functions in a supplementary manner with respect to forcing locking ring 114 towards a position where a clamping force is exerted. In addition, Figure 5 shows a link 54 for operating shaft 26 either mechanically or manually, in conjunction with spring action 60. A feature which can be used with the first embodiment is a structure within the clamp member to assist in the unclamping process, such as plungers 36 which act under the influence of springs 38 (see, for example, Figure 3). As can easily be seen due to its orientation, the plunger is pressed by the spring against the clamp header 16. This causes a small restoring force ( i.e. , less than the clamping force) which acts opposite to the clamping force to assist in pushing the clamp member 32 away from the work piece when clamping action is no longer desired. The cam clamp, as described in these or in any other embodiment, can be mounted, to a workbench or worktable 42 (see Figure 3), for example, in any known manner, such as screws 30 or T-blocks 56 fixed to the clamp base by screws 58, and inserted into T-slots. Other embodiments of the invention are certainly possible. For example, Figure 6 shows a double clamp assembly 210 driven by dual piston cylinders 248, 248 which are actuated from a unified pressure source 211 therebetween. In another arrangement (not shown), the auxiliary driving source can be oriented at any angle with respect to the clamp, seen from a top plan view. Certain applications may require greater clamping force than available through the first embodiment described above. In such instances, motive force from a suitable source is applied directly to the central shaft 12 in addition to the locking cam 14. In this manner, greater clamping force is achieved compared to the application of force only on the locking cam 14. Figure 7 illustrates an alternative whereby motive force is exerted directly to the central shaft 12, by pressure from pressure port 63 for example, in addition to the locking cam 14 in a direction to cause a clamping force to be exerted. Thus, in such an example, the clamping force exerted to the action of the locking cam 14 is increased by the application of additional force directly to the central shaft 12. Dish springs 65 are used to provide the return of the central shaft, as seen in Figure 7.

Claims: A cam clamp comprising: (a) a clamp header (16); (b) a base (18); (c) a central shaft (12) disposed within said clamp header, said central shaft having a longitudinal axis therealong, said central shaft being rotatable about said longitudinal axis and axially moveable; (d) a clamp member (32) mounted on an axial end of said central shaft; characterized by: (e) an opposite cam (20) mounted at the opposite axial end of said central shaft by a nut (28), said opposite cam being disposed in said base and being axially moveable; (f) a locking cam (14) disposed within said clamp header, said locking cam being in a plane substantially perpendicular to said axis of said central shaft (12) and having at least one surface which faces said opposite cam (20) and which is at least partially inclined relative to said longitudinal axis away from said base, said locking cam being linearly moveable within said plane and including engaging means (22) mounted thereon for engaging said locking cam (14) to said central shaft (12) to cause said central shaft and clamp member to rotate about said longitudinal axis through a certain arclength of travel; and (g) auxiliary driving means (26, 48), connected to said locking cam, for moving said locking cam within said clamp header during operation. A cam clamp according to claim 1, wherein said certain arclength of travel is between a first clamp position where no clamping force is exerted by said clamp member (32) and a second clamp position, spaced rotationally apart from said first clamp position, where a clamping force is exerted. A cam clamp according to claim 1, wherein said engaging means comprises a pin (22) mounted on said locking cam. A cam clamp according to claim 2, wherein said clamp header (16) is provided with stop means (24) for preventing said central shaft (12) and said clamp member (32) from rotating beyond said second clamp position from said first clamp position. A cam clamp according to claim 4, wherein said stop means comprises a pin (24) mounted on said clamp header (16). A cam clamp according to claim 1, wherein said clamp member includes deformable spring means (38) for providing a restoring force counteracting said clamping force exerted by said clamp member (32) in operation for facilitating the release of said clamp member from an object being clamped when said clamping force is no longer applied. A cam clamp according to claim 1, wherein said auxiliary driving means comprises a pressurizable cylinder (48). A cam clamp according to claim 7, wherein said pressurizable cylinder (48) is pneumatically operated. A cam clamp according to claim 8, wherein the pneumatic fluid is nitrogen gas. A cam clamp according to claim 7, wherein said pressurizable cylinder (48) is hydraulically operated. A cam clamp according to claim 1, wherein said auxiliary driving means comprises a mechanical power source (54) connected to said locking cam (14). A cam clamp according to claim 1, including resilient spring means (60) for acting upon said locking cam to actuate said clamp member during a clamping process, said auxiliary driving means (26, 48) being operative during an unclamping process. A cam clamp according to claim 1, including gas pressure means (60) for acting upon said locking cam to actuate said clamp member during a clamping process, said auxiliary driving means (26, 48) being operative during an unclamping process. A cam clamp according claim 1, said cam clamp further comprising spring means for moving said locking cam during a clamping process, whereby said auxiliary driving means is used to move said locking cam during an unclamping process. A cam clamp according to claim 1, further comprising means (63) for applying motive force to said locking cam and directly to said central shaft to actuate a clamping process, thereby causing said clamp member to exert a relatively stronger clamping force compared to actuation of said clamping process by said locking cam alone.

Inventors: DE SOUSA MONTEIRO LUCIANO TRIN, DE SOUSA MONTEIRO, LUCIANO TRINDADE
Applicants: SOUSA MONTEIRO LUCIANO TRINDAD, DE SOUSA MONTEIRO, LUCIANO TRINDADE
Application year: 1993
Main classification: B25B5
IPC codes: B25B5