Cooling module for linear motors

Abstract

Cooling module for linear motors, including: a main body (10) comprising a first circuit board section (11) and a second circuit board section (12), wherein the first end face (111) of the first circuit board section (11) and the second end face (121) of the second circuit board section (12) overlap along the direction of an imaginary first axis (Z); a flow channel (20) provided in the main body (10), wherein the shape of the flow channel (20) is defined between the first end surface (111) and the second end surface (121) and has a predetermined height (T) on the first axis (Z); at least one flow vortex element (50) located in the flow channel (20) and having a first projection (51) and a second projection (52), wherein the first projection (51) extends from the first end surface (111) towards the second end surface (121) along the direction of the first axis (Z) by a first height (tf ) protrudes, a first deflection space (512) is formed between the extension end of the first projection (51) and the second end surface (121), the second projection (52) and the first projection (51) are partially offset from each other on the second end surface (121) along the forward projection of the first axis (Z) on the second end surface (121) and are offset in the direction of the first end surface (111) along the direction of the first axis (Z) by a second height (t) r ) protrudes, a second deflection space (522) is formed between the extension end of the second projection (52) and the first end surface (111) and the sum of the first height (t f ) and the second height (t r ) less than or equal to the height (T) of the flow channel (20); wherein the outline shapes of the first projection (51) and the second projection (52) are symmetrical to each other, the first projection (51) and the second projection (52) each have a first end (513), a second end (515) and a connecting section located between the first end (513) and the second end (515), the forward projection of the first end (513) of the first projection (51) on the second end surface (121) partially overlaps the first end (513) of the second projection (52), the forward projection of the second end (515) of the first projection (51) on the second end surface (121) and the second end (515) of the second projection (52) are offset from each other, and a first deflection surface (516) is provided on two opposite sides of the first projection (51) and the second projection (52).

Description

Field of invention

[0001] The present invention relates to a cooling technology and in particular a cooling module for linear motors. State of the art

[0002] Linear motors typically generate large amounts of heat during operation and therefore require cooling to maintain the correct operating temperature. Common systems use a cooling fluid that flows through the motor's heat dissipation section to absorb heat and then transfer it away from the motor, thus keeping the motor temperature within an acceptable range.

[0003] The cooling fluid usually flows very stably in the flow channel, with the temperature being higher in the section near the motor and lower in the section far from the motor, which leads to an uneven temperature distribution and thus impairs the cooling effect.

[0004] Therefore, Japanese patent application JP 2021-164 193 A discloses that several projections are provided in the flow channel for dividing the cooling fluid into multiple streams. The projections disclosed in Japanese patent application JP 2004-260 941 A are wing-shaped and located at the turning points of the flow channel, serving to guide the flow direction of the cooling fluid. However, the flow of the cooling fluid disclosed in these applications does not result in any significant turbulent flow. The problem of uneven temperature distribution still exists in both of these patents.

[0005] In addition, a liquid cooling system for an electric machine is known from DE 10 2018 206 012 A1, comprising a stator arrangement and a rotor arrangement, wherein the stator arrangement is provided with a cooling channel and / or wherein the rotor arrangement is provided with a cooling channel, wherein a fluid flows through the cooling channel in a main flow direction, wherein the cooling channel provides at least one groove (20).

[0006] DE 10 2016 216 019 A1 discloses an insert for a cooling jacket of an electric machine. The insert comprises a flat base body and at least one flow element.

[0007] From DE 199 28 023 A1, an alternating current generator is known which comprises a housing having a chamber for the circulation of a fluid and an outlet channel for the fluid adjacent to the chamber. The housing also includes a deflector element to direct the fluid towards the channel. Object of the invention

[0008] The invention is based on the objective of eliminating the problems of uneven temperature distribution and poor cooling effect and providing a cooling module for linear motors with which a turbulent flow can be generated when the cooling fluid flows.

[0009] To solve the above-mentioned problem, the present invention provides a cooling module for linear motors, the main technical feature of which is that at least one flow turbulence element is arranged in a flow channel, wherein the flow turbulence element has a first projection and a second projection which are offset from each other and the two projections extend opposite to the center of the flow channel, whereby the cooling fluid flowing through the flow turbulence element is blocked by the first projection or the second projection and thus a turbulent flow is generated.

[0010] To achieve the above technical characteristics, the cooling module for linear motors further comprises a main body having a first circuit board section and a second circuit board section, wherein the first end face of the first circuit board section and the second end face of the second circuit board section overlap each other along the direction of an imaginary first axis, wherein the flow channel is provided in the main body, the shape of the flow channel between the first end face and the second end face is defined, and the flow channel has a predetermined height (T) on the first axis, wherein a respective flow vortex element is located in the flow channel and has a first projection and a second projection, the first projection extending from the first end face towards the second end face along the direction of the first axis by a first height (t). f) protrudes, a first deflection space is formed between the extension end of the first projection and the second end surface, the second projection and the first projection are partially offset from each other on the second end surface along the forward projection of the first axis on the second end surface and are offset in the direction of the first end surface along the direction of the first axis by a second height (t r ) protrude, a second deflection space is formed between the extension end of the second projection and the first end surface, and the sum of the first height (t f ) and the second height (t r) less than or equal to the height (T) of the flow channel, wherein the outline shapes of the first projection and the second projection are symmetrical to each other, the first projection and the second projection each have a first end, a second end and a connecting section located between the first end and the second end, the forward projection of the first end of the first projection on the second end surface partially overlaps the first end of the second projection, the forward projection of the second end of the first projection on the second end surface and the second end of the second projection are offset from each other, and a first deflection surface is provided on two opposite sides of the first projection and the second projection. Brief description of the drawings Fig. Figure 1 shows a schematic view according to a first embodiment of the cooling module for linear motors according to the invention; Fig. Figure 1A shows an enlarged partial view of a single flow vortex element according to Fig. 1; Fig. Figure 2 shows a schematic perspective exploded view according to Fig. 1; Fig. Figure 3 shows a perspective view of a first projection according to Fig. 2; Fig. Figure 4 shows a perspective view of a second projection according to Fig. 2; Fig. Figure 5 shows a section view along the section line 5-5 according to Fig. 1; Fig. 5A shows a section view along the section line 5A-5A according to Fig. 1A; Fig. Figure 5B shows a section view along the section line 5B-5B according to Fig. 1A; Fig. Figure 6A shows a sectional view along section line 6-6 according to Fig. 1; Fig. Figure 6B shows a schematic view of another embodiment according to Fig. 6A, in which there is a distance between each first lead and the corresponding second lead; Fig. 7 shows a different sectional view according to Fig. 1; Fig. Figure 8 shows an enlarged partial view according to Fig. 1; Fig. Figure 9 shows a perspective view of a flow vortex element according to Fig. 1; Fig. Figure 10 shows experimental data demonstrating the heat dissipation effect at different ratios between the radius (Rt) of the first circular structure and the width (W) of the flow channel; Fig. Figure 11 shows experimental data demonstrating the heat dissipation effect of flow turbulence elements at different positions in the flow channel; Fig. Figure 12 shows experimental data demonstrating the heat dissipation effect of flow vortex elements of different sizes; Fig. Figure 13 shows experimental data demonstrating the heat dissipation effect of a first projection at different angles; Fig. Figure 14 shows experimental data demonstrating the heat dissipation effect with different numbers of flow turbulence elements; Fig. Figure 15 shows experimental data demonstrating the heat dissipation effect of two adjacent flow vortex elements at different distances; Fig. Figure 16 shows experimental data demonstrating the heat dissipation effect of flow vortex elements arranged with or without a distance between them; Fig. Figure 17 shows the different forms of a first projection according to the changes in the curvature of the connecting section, the size of the connecting section, the radius (Rt) and the radius (Rh); Fig. Figure 18 shows a schematic view of a flow vortex element and the flow channel according to a second embodiment of the present invention; Fig. Figure 19 shows a schematic view of a first projection according to a third embodiment of the present invention; Fig. Figure 20 shows a schematic view of a first projection according to a fourth embodiment of the present invention; Fig. Figure 21 shows a schematic view of the flow channel according to a fifth embodiment of the present invention; Fig. Figure 22 shows a perspective exploded view of the main body according to a sixth embodiment of the present invention. Detailed description of the exemplary implementations

[0011] It will be directed to the Fig. Reference is made to Figures 1 to 9, which show a cooling module for linear motors according to a first embodiment of the present invention. It is designed for mounting on a linear motor (not shown) to achieve heat dissipation and cooling. The cooling module for linear motors comprises a main body (10), a flow channel (20), an inlet (30), an outlet (40), and several flow turbulence elements (50).

[0012] The main body (10) has a first board section (11) and a second board section (12), wherein the first end surface (111) of the first board section (11) and the second end surface (121) of the second board section (12) overlap along the direction of an imaginary first axis (Z).

[0013] The flow channel (20) is defined by a recessed groove on the first end surface (111) and the second end surface (121) and can extend arbitrarily within the main body (10). As in Fig. As shown in Figure 1, various segments of the flow channel (20) extend along an imaginary second axis (Y) and a third axis (X), respectively, with the second axis (Y) and the third axis (X) each being perpendicular to the first axis (Z) and the second axis (Y) and the third axis (X) each running parallel to the plane formed by the first end surface (111) and the second end surface (121), respectively. The inlet (30) is located on the first circuit board section (11) and is continuously connected to the starting point (21) of the flow channel (20) and the outer surface of the main body (10). The outlet (40) is located on the first circuit board section (11) and is continuously connected to an end point (22) of the flow channel (20) and the outer surface of the main body (10). A cooling fluid can flow through the continuous connection between the inlet (30), the flow channel (20) and the outlet (40).

[0014] To simplify the description, only the part within the dashed frame will be discussed below. Fig. The section of the flow channel (20) located at 1 is described. The flow channel (20) has a predetermined length (L) on the second axis (Y), a predetermined width (W) on the third axis (X) and a predetermined height (T) on the first axis (Z).

[0015] The flow vortex elements (50) are located in the flow channel (20) and satisfy the condition that the length (L) of the flow channel (20) is greater than or equal to the width (W) of the flow channel (20). Each flow vortex element (50) has a first projection (51) and a second projection (52), the first projection (51) extending from the first end face (111) towards the second end face (121) along the direction of the first axis (Z) by a first height (t). f) protrudes, wherein a first deflection space (512) is formed between the extension end (511) of the first projection (51) and the second end surface (121), and the second projection (52) and the first projection (51) are partially offset from each other on the second end surface (121) along the forward projection of the first axis (Z) on the second end surface (121) and are offset in the direction of the first end surface (111) along the direction of the first axis (Z) by a second height (t) r ) projecting, wherein a second deflection space (522) is formed between the extension end (521) of the second projection (52) and the first end surface (111), wherein the sum of the first height (t f ) and the second height (t r ) less than or equal to the height (T) of the flow channel (20). As in the Fig. 6A and Fig. As shown in 6B, the distance (G) between the extension end (511) of the first projection (51) and the extension end (521) of the second projection (52) on the first axis (Z) gives the first height (t f ), the second height (t r ) and the height (T) of the flow channel (20) the following formula (1): G=T−(tf+tr), where G can be 0

[0016] Furthermore, if the first height (t f ) and the second height (t r If the flow turbulence element (50) is too small, the processing yield may be low. Maintaining the integrity of the flow turbulence element (50) is then difficult. To address this, a test was performed to determine whether a flow turbulence element (50) is present and whether the distance (G) between the flow turbulence elements (50) is zero or not zero. The experimental results are presented in Fig. 16 shown. The first height (t f ), the second height (t r) and the height (T) of the flow channel (20) result in the following formula (2): tf≥0.2×T; tr≥0.2×T; α=tf+trT; where α lies between 0.4 and 1

[0017] The offset mentioned above means that the positional relationship between the first lead (51) and the second lead (52) can be staggered, offset, etc., but is not limited to, as in the Fig. 3, Fig. 4 and Fig. Figure 9 shows. In the present embodiment, the outline shapes of the first projection (51) and the second projection (52) are symmetrical to each other, wherein the first projection and the second projection each have a first end (513, 523), a connecting section (514, 524), a second end (515, 525), a first deflection surface (516, 526) and a second deflection surface (517, 527), wherein the connecting section (514, 524) bridges the first end (513, 523) and the second end (515, 525), and the two sides of a connecting section (514, 524) facing away from each other in the direction of extension each represent a first deflection surface (516, 526) and a second deflection surface (517, 527).the second deflection surface (517) of the first projection (51) and the second deflection surface (527) of the second projection (52) are opposite each other along the forward projection of the first axis (Z) on the second end surface (121), and the first deflection surface (516) of the first projection (51) and the first deflection surface (526) of the second projection (52) are facing away from each other along the forward projection of the first axis (Z) on the second end surface (121), as in , Fig. 9 shown. Here, each first deflection surface (516, 526) has a first radius of curvature and each second deflection surface (517, 527) has a second radius of curvature.

[0018] The first end (513) of the first projection (51) and the first end (523) of the second projection (52) each form a first circular structure in the cross-section of the second axis (Y), and their forward projections along the first axis (Z) on the second end face (121) overlap, with the first circular structures having the same radius (Rt). According to the in Fig. As shown in the experimental results shown in Figure 10, the temperature increases considerably and the heat dissipation effect is impaired when the ratio of the radius (Rt) to the width (W) of the flow channel (20) is > 18%. If the radius (Rt) is too small, processing becomes difficult and the yield decreases. Accordingly, the radius (Rt) and the width (W) of the flow channel (20) give the following formula (3): Rt / W≤18%, where Rt≥0.5 mm

[0019] According to the in Fig. As shown in the experimental results shown in Figure 11, the temperature increases considerably when the distance (Wt) between the geometric center of the overlapping section of the first projection (51) and the second projection (52) and the center line (O) of the flow channel (20), which runs parallel to the second axis (Y), is greater than or equal to 15% of the width (W) of the flow channel (20). Accordingly, the distance (Wt) and the width (W) of the flow channel (20) give the following formula (4): 0%≤Wt / W≤15%

[0020] In other words, the position of each flow vortex element (50) is shifted by the distance (Wt) from the centerline (O) of the flow channel (20) in the direction of the first end surface (111) or the second end surface (121). The calculation is based on W / 2 ± Wt.

[0021] The second end (515) of the first projection (51) and the second end (525) of the second projection (52) each form a second circular structure in the cross-section of the second axis (Y), these second circular structures having the same radius (Rh) and the forward projection of the second end (515) of the first projection (51) on the second end face (121) and the second end (525) of the second projection (52) being offset from each other. According to the in Fig. As shown in the experimental results of Figure 12, the heat dissipation effect is better when the ratio between the distance (K) between the second end (515) of the first projection (51) and the imaginary line (F) running along the second axis (Y) from the geometric center of the overlapping section of the first projection (51) and the second projection (52), and the minimum distance (E) between the first end (513) and the second end (515) of the first projection (51) along the second axis (Y) is higher, but this is limited by the specific dimensions. Thus, the distance (K) and the distance (E) give the following formula (5): E / K≥1

[0022] According to formulas (3) and (5), the limits of change of various numerical values ​​can be determined, in particular the radius (Rt), the width (W) of the flow channel (20), the first radius of curvature, and the second radius of curvature. In conjunction with changes in the radius (Rh), several flow vortex elements (50) with different shapes can be obtained, such as several variations of the first projection (51), which are in Fig. Figure 17 shows, but is not limited to, the first radius of curvature. The limiting region of the first radius of curvature is 1.25Rt ≤ first radius of curvature ≤ 60Rt, where the limiting region of the second radius of curvature can be the same as the limiting region of the first radius of curvature or can be slightly varied.

[0023] As in Fig. As shown in Figure 8, a first included angle (β1) exists between the connecting line between the first end (513) and the second end (515) of the first projection (51) and the imaginary line (F) running along the second axis (Y) from the geometric center of the overlapping section of the first projection (51) and the second projection (52). A test was performed using the first included angle (β1) as an example, where β1 = 45° is the control group and other different angles are the experimental group. The test results are shown in Figure 8. Fig. Figure 13 illustrates this. If β1 ≤ 35°, the temperature increases; if the angle β ≥ 65°, the temperature is also higher than that of the control group. Accordingly, the first included angle (β1) is defined as being between 35° and 65°.

[0024] Furthermore, between the connecting line between the first end (523) of the second projection (52) and the second end (525) of the second projection (52) and the imaginary line (F) running along the second axis (Y) from the geometric center of the overlapping section of the first projection (51) and the second projection (52), there exists a second included angle (β2), the second included angle (β2) also being between 35° and 65°.

[0025] The in Fig. According to the test results shown in Figure 14, the heat dissipation effect is better the more flow vortex elements (50) are arranged in the flow channel (20). Furthermore, according to the results shown in Figure 14, the following applies: Fig. The experimental results shown in Figure 15 demonstrate that the temperature begins to decrease when the ratio between the distance (P) between any two adjacent flow vortex elements (50) along the second axis (Y) and the width (W) of the flow channel (20) is ≥ 1. When P / W is ≥ 2, the temperature begins to rise. Furthermore, an excessively large distance (P) leads to a reduction in the total number of flow vortex elements (50) and thus to an impairment of the flow vortex effect. The distance (P) and the width (W) of the flow channel (20) are given by the following formula (6): 1≤P / W≤2

[0026] Based on the description of the above structure, the specific use of the present invention is described below: As in Fig. As shown in Figure 1A, the external cooling fluid is blocked and deflected as it flows through the overlapping section of the first projection (51) and the second projection (52), generating a first horizontal flow turbulence (P1) and a second horizontal flow turbulence (P2) in the directions of the second axis (Y) and the third axis (X).

[0027] Part of the first horizontal flow vortex (P1) is separated from the second horizontal flow vortex (P2) along the first deflection surface (516) of the first projection (51). The other part of the first horizontal flow vortex (P1) extends along the outline of the extension end (511) of the first projection (51), whereby the external cooling fluid changes its position in the flow channel (20) on the first axis (Z) and flows into the first deflection chamber (512), thereby forming a first vertical flow vortex (H1) in the direction of the first axis (Z), as shown in Fig. 5A shown.

[0028] Part of the second horizontal flow vortex (P2) is separated from the first horizontal flow vortex (P1) along the second deflection surface (526) of the second projection (52). The other part of the second horizontal flow vortex (P2) extends along the outline of the extension end (521) of the second projection (52), whereby the external cooling fluid changes its position in the flow channel (20) on the first axis (Z) and flows into the second deflection space (522), thereby forming a second vertical flow vortex (H2) in the direction of the first axis (Z), as shown in Fig. 5B shown.

[0029] Fig. Figure 18 shows a second embodiment of the present invention. The difference from the first embodiment is that the forward projection of the first circular structure of the first projection (51A) on the second end surface (121A) partially overlaps with the first circular structure of the second projection (52A). In other words, the forward projection of the first circular structure of the first projection (51A) on the second end surface (121A) is tangential to the first circular structure of the second projection (52A) along the first axis (Z). The distance between the centers of curvature of the first circular structures (Wg) and the radius of the first circular structure (Rt) give the following formula (7): Wg≤2×Rt−1, where Wg is not 0

[0030] The distance (Y) between the second end (515A) of the first projection (51A) and the second end (525A) of the second projection (52A), the width (W) of the flow channel (20A), the radius (Rt) of the first circular structure and the distance between the centers of curvature (Wg) of the first circular structures give the following formula (8): 2×Rt+Wg≤Y≤W

[0031] The difference between the third embodiment of the present invention and the first embodiment lies in the change in the shape of the flow turbulence element. Using the first projection (51B) as an example, Fig. Figure 19 shows that the second end (515B) of the first projection (51B) has a rectangular structure in the cross-section of the second axis (Y), with the second deflection surface (517B) running along a straight line and the first deflection surface (516B) still running along an arc-shaped line. The shape of the second projection is the same as that of the first projection (51B) and is therefore not described again here.

[0032] Fig. Figure 20 shows a fourth embodiment of the present invention. The difference from the third embodiment is that both the first deflection surface (516C) and the second deflection surface (517C) run along a straight line.

[0033] Fig. Figure 21 shows the fifth embodiment of the present invention. The difference from the first embodiment is that the flow channel (20D) has a first straight line segment (23) and a second straight line segment (24) adjacent to the first straight line segment (23), wherein the first straight line segment (23) extends along the direction of the second axis (Y) and there is a deflection angle (θ) between the extension direction of the second straight line segment (24) and the second axis (Y). If the deflection angle (θ), the length (L1) of the first straight line segment (23), the length (L2) of the second straight line segment (24), and the width (W) of the flow channel (20D) yield the following formula (9), the flow vortex elements (not shown) may be located in the first straight line segment (23) or in the second straight line segment (24): θ<3°;L1+L2≥W

[0034] Fig.Figure 22 shows the sixth embodiment of the present invention. The difference from the first embodiment is that the main body (10E) further comprises a third circuit board section (13) located between the first circuit board section (11E) and the second circuit board section (12E), wherein the third circuit board section (13) is provided with a cavity (131) and the flow channel (not shown) is defined by the cavity (131), the first end surface (111E) and the second end surface (121E). Reference symbol list 10, 10E Main body 11, 11E first circuit board section 111, 111E first end surface 12, 12E second circuit board section 121, 121A, 121E second end surface 13 third circuit board section 131 Cavity 20, 20D flow channel 21 Starting point 22 Endpoint 23 first straight line segment 24 second straight line segment 30 Admission 40 outlet 50 Flow turbulence element 51, 51A, 51B first lead 511 End of extension 512 first diversion room 52, 52A second lead 521 End of extension 522 second diversion room 513, 523 first end 514, 514B, 514C, 524 Connection section 515, 515A, 515B, 525, 525A second end 516, 516B, 516C, 526 first deflection surface 517, 517B, 517C, 527 second deflection surface Z first axis Y second axis X third axis Length L T height W width t f first height t r second height Rt, Rh radius Wt, Y, Wg, K, E, P distance β1 first included angle β2 second included angle θ deflection angle L1, L2 length O Center line F imaginary line P1 first horizontal flow turbulence P2 second horizontal flow turbulence H1 first vertical flow turbulence H2 second vertical flow turbulence

Claims

[1] Cooling module for linear motors, comprising: a main body (10) comprising a first circuit board section (11) and a second circuit board section (12), wherein the first end face (111) of the first circuit board section (11) and the second end face (121) of the second circuit board section (12) overlap along the direction of an imaginary first axis (Z); a flow channel (20) provided in the main body (10), wherein the shape of the flow channel (20) is defined between the first end surface (111) and the second end surface (121) and has a predetermined height (T) on the first axis (Z); at least one flow vortex element (50) located in the flow channel (20) and having a first projection (51) and a second projection (52), wherein the first projection (51) extends from the first end surface (111) towards the second end surface (121) along the direction of the first axis (Z) by a first height (tf ) protrudes, a first deflection space (512) is formed between the extension end of the first projection (51) and the second end surface (121), the second projection (52) and the first projection (51) are partially offset from each other on the second end surface (121) along the forward projection of the first axis (Z) on the second end surface (121) and are offset in the direction of the first end surface (111) along the direction of the first axis (Z) by a second height (t) r ) protrudes, a second deflection space (522) is formed between the extension end of the second projection (52) and the first end surface (111) and the sum of the first height (t f ) and the second height (t r ) less than or equal to the height (T) of the flow channel (20); wherein the outline shapes of the first projection (51) and the second projection (52) are symmetrical to each other, the first projection (51) and the second projection (52) each have a first end (513), a second end (515) and a connecting section located between the first end (513) and the second end (515), the forward projection of the first end (513) of the first projection (51) on the second end surface (121) partially overlaps the first end (513) of the second projection (52), the forward projection of the second end (515) of the first projection (51) on the second end surface (121) and the second end (515) of the second projection (52) are offset from each other, and a first deflection surface (516) is provided on two opposite sides of the first projection (51) and the second projection (52). [2] Cooling module for linear motors according to claim 1, wherein the flow channel (20) has a predetermined length (L) on an imaginary second axis (Y) and a predetermined width (W) on an imaginary third axis (X) so that an external cooling fluid can flow in the flow channel (20), wherein the second axis (Y) and the third axis (X) are each perpendicular to the first axis (Z) and the second axis (Y) and the third axis (X) are each parallel to the plane formed by the first end surface (111) and the second end surface (121), respectively. [3] Cooling module for linear motors according to claim 2, wherein a first included angle exists between the connecting line between the first end (513) of the first projection (51) and the second end (515) of the first projection (51) and the imaginary line extending along the second axis (Y) from the geometric center of the overlapping section of the first projection (51) and the second projection (52), wherein the first included angle is between 35° and 65°, and wherein a second included angle exists between the connecting line between the first end (513) of the second projection (52) and the second end (515) of the second projection (52) and the imaginary line extending along the second axis (Y) from the geometric center of the overlapping section of the first projection (51) and the second projection (52), wherein the second included angle is between 35° and 65°. [4] Cooling module for linear motors according to claim 2, wherein the first end (513) of the first projection (51) and the first end (513) of the second projection (52) each form a first circular structure in the cross-section of the second axis (Y), wherein the first circular structures have the same radius (Rt), wherein the radius (Rt) and the width (W) of the flow channel (20) yield the following formula: Rt / W≤18%, where Rt≥0.5 mm. [5] Cooling module for linear motors according to claim 4, wherein the forward projection of the first circular structure of the first projection on the second end surface along the first axis is tangential to the first circular structure of the second projection, wherein the distance between the centers of curvature of the first circular structures (Wg) and the radius of the first circular structure (Rt) yield the following formula: Wg≤2×Rt−1, where Wg is not 0. [6] Cooling module for linear motors according to claim 4, wherein the distance (Y) between the second end (515) of the first projection (51) and the second end (515) of the second projection (52), the width (W) of the flow channel (20), the radius (Rt) of the first circular structure and the distance between the centers of curvature (Wg) of the first circular structures yield the following formula: 2×Rt+Wg≤Y≤W. [7] Cooling module for linear motors according to claim 2, wherein the flow turbulence elements (50) are located in the segments of the flow channel (20), the length (L) of which is provided on the second axis (Y) is greater than or equal to the width (W) of the flow channel (20). [8] Cooling module for linear motors according to claim 2, wherein the flow channel (20) has a first straight line segment (23) and a second straight line segment (24) adjacent to the first straight line segment (23), wherein the first straight line segment (23) extends along the direction of the second axis (Y) and there is a deflection angle (θ) between the extension direction of the second straight line segment (24) and the second axis (Y), wherein, if the deflection angle (θ), the length (L1) of the first straight line segment (23), the length (L2) of the second straight line segment (24) and the width (W) of the flow channel (20) result in the following formula, the flow vortex elements (50) may be located in the first straight line segment (23) or in the second straight line segment (24): θ<3°;L1+L2≥W. [9] Cooling module for linear motors according to claim 2, wherein the distance (Wt) between the geometric center of the overlapping section of the first projection (51) and the second projection (52) and the center line of the flow channel (20) running parallel to the second axis (Y), and the width (W) of the flow channel (20) yield the following formula: 0%≤Wt / W≤15%. [10] Cooling module for linear motors according to claim 2, wherein the ratio between the distance (K) between the second end (515) of the first projection (51) and the imaginary line running along the second axis (Y) from the geometric center of the overlapping section of the first projection (51) and the second projection (52), and the minimum distance (E) between the first end (513) and the second end (515) of the first projection (51) along the second axis (Y) yields the following formula: E / K≥1. [11] Cooling module for linear motors according to claim 2, wherein the distance (G) between the extension end of the first projection (51) and the extension end of the second projection (52) on the first axis (Z), the first height (t f ), the second height (t r ) and the height (T) of the flow channel (20) yield the following formula: G=T−(tf+tr), where G can be 0. [12] Cooling module for linear motors according to claim 2, wherein the first height (t f ), the second height (t r ) and the height (T) of the flow channel (20) yield the following formula: tf≥0,2×T;tr≥0,2×T;α=tf+trT; where α lies between 0,4 and 1. [13] Cooling module for linear motors according to claim 2, wherein the number of flow turbulence elements (50) is two, the distance (P) between the two flow turbulence elements (50) along the second axis (Y) and the width (W) of the flow channel (20) yield the following formula: 1≤P / W≤2.

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