Abstract: Abstract: In order to satisfy the pressing and rubbing operation effects of barking machines and simplify its mechanical structure, a curved groove ball bearing was designed. The outer ring of curved groove ball bearing was a three-dimensional sine curve circular arc raceway with a period of 7 and an amplitude of 1 mm. The inner ring of curved groove ball bearing was designed as a fixed ball hole structure. The curved groove ball bearings were installed in pairs, the center axis of the two bearings needed to be lined up properly, and its installation should be ensured the “Peak” to the “Valley”. The rotation of the inner ring was driven by spindle rotation in operation, the rolling element moved into the inner ring ball socket, at the same time, moved along the outer ring raceway. That formed gyratory motions and straight reciprocating motions of the shaft. The main structural parameters of curved groove ball bearing were as follows: outer diameter 80 mm, inner diameter 50 mm, width 16 mm, radius of outer ring raceway 5 mm, radius of spherical cavity 5.9 mm, small ball diameter in spherical cavity 1 mm, curvature radius of small ball fixed point 4.9 mm, roller diameter 9.525 mm, rolling number 7, and original contact angle 25°. The raceway of outer ring affects not only the motion characteristics of curved groove ball bearing but also its carrying capacity. The contact stress of five contact points between rolling element and peak to bottom of outer ring raceway under different loading forces was analyzed, and force analysis model of the curved groove ball bearing was established. Theoretical arithmetic results showed that the contact stress between the rolling element and the outer ring was decreased from peak to valley, and increased by the loading force. Base on theoretical analysis, curved groove ball bearing was designed. A self-made test bench was used to test the curved groove ball bearing samples. The test bench exerted a radial force upon the bearing by weight loading methods, and exerted an axial force by adjusting the amount of spring compression. A phase adjustable bearing seat was adopted on the test bench. The installation phase of the two bearings could be adjusted by nuts to ensure the synchronous movement of the two bearings and avoid the interference of the movement. The curved groove ball bearing was applied to the professional equipment of agricultural products processing and utilization, the requirements of the running speed was not too high, and considering the machining precision during the trial, therefor the test bearing was tested at a low speed. The spindle speed of test bench was controlled by frequency converter. The test bearings operated at speeds of 60 r/min. The thermocouple was attached to the bottom of the outer ring for temperature detection. The outer ring temperature rising processes were tested in the radial force 150 N under the condition of axial load for outer ring 80, 120, 160, 200 and 235 N, and in the axial force160 N under the condition of radial force for outer ring 50, 100, 150, 200 and 250 N. The self-made curved groove ball bearing is stable and reliable during the tests. The results showed that the temperature rising range of bearing outer ring with the increase of loading forces s was heightened, and the temperature rise speed was accelerated. The temperature rise curve suddenly increased in the beginning of 5 min, and reached 80% of the stable temperature rise. The temperature rise curve tends to be gentle and basically reached the thermal equilibrium state after 10 min. Our research provides the reference for the structure optimization, shaping production and subsequent application of the curved groove ball bearing.