JPS59141704A - Propelling motor - Google Patents

Abstract

PURPOSE:To make available the generation of propelling forces with a simple constitution, by arranging such that a heavy weight pivotable in a restricted manner about a pivot axis may vary at least either a pivot radius or an angular velocity at every one pivot. CONSTITUTION:Links 20, 21 of upper chamber 12 rotate in a forward direction, whereas links 20, 21 of lower chamber 13 rotate in a reverse direction. The rotary driving force of a motor 26 is divided by a bevel gear mechanism 25 into an upper chamber 12 side and a lower chamber 13 side for their respective rotation in the forward and the reverse directions. A first link 20 is rotated in the forward and reverse directions at the equal velocity via a chain 24, a sprocket 23 and a pivot axis 22. In response to the rotation of first link 20, a spur gear 32 rotates around a spur gear 34 and a second ring 21 rotates via a sprocket 31, a chain 30, a sprocket 29 and an axis 28. Thus, a combined reaction is created on the pivot axis 22, thereby obtaining vibratory propelling forces in the horizontal direction.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a propulsion motor that utilizes centrifugal force.

Generally, when a weight is restrained and rotated, a centrifugal force of (mrω2) is generated. Therefore, the present inventor focused on the fact that thrust can be obtained by extracting such centrifugal force in one direction under certain conditions, and completed the present invention. The constant condition is that the weight, which can be restrained and rotated about the rotation axis, is changed in either the radius of rotation or the angular velocity each time it makes a rotation.

First, the present invention will be explained in detail.

In Fig. 1, the first link 1 and the second link 2 are connected at their ends by a shaft 3, and a weight 4 is attached to the tip of the second link 2, and the first link 1 is a pivot shaft. The second link 2 can be rotated around a shaft 3, and the second link 2 can be driven to rotate around a shaft 3. That is, the weight 4 can rotate around the pivot shaft 5 while rotating around the shaft 3.

Now, the length of the first link 1 is 5QQmi, and the weight is 100.
0F! , the length of the second link 2 is 500wn1, the weight is 50
0f! , the weight of shaft 3 is 1000f! , the weight of weight 4 is 5
0005', and the first link 1 is rotated clockwise at 60 rpm around the rotation axis 5, and the second link 2 is rotated clockwise around the axis 3 at 5 Q rpm (hereinafter referred to as normal rotation) at the same time. do.

Figure 2 shows the first link 1. FIG. 3 schematically shows the movement of the second link 2, and a graph showing the displacement of the weight 4 at this time. In FIG. 3, A indicates displacement in the X-axis direction, B indicates displacement in the Y-axis direction, and C indicates displacement in the Z-axis direction (direction perpendicular to the plane of the paper in FIG. 2). Furthermore, centrifugal force acts on the weight 4, and FIG. 4 shows this as a reaction force acting on the pivot shaft 5. In FIG. 4, A indicates the reaction force in the X-axis direction, and B indicates the reaction force in the Y-axis direction.

Furthermore, FIG. 5 is a graph showing the reaction force acting on the shaft 3. The middle person in FIG. 5 similarly shows the reaction force in the X-axis direction, and B shows the reaction force in the Y-axis direction. FIG. 6 is a graph showing the absolute value of the reaction force acting on the pivot shaft 5 in the X-axis direction. FIG. 7 is a graph showing the absolute value of the reaction force acting on the shaft 3 in the X-axis direction.

On the other hand, on the contrary, the first link 1. When the second links 2 are rotated counterclockwise at the same time (hereinafter referred to as reverse rotation), a schematic diagram of the movement is shown in Figure 8, and the displacement of the weight 4 is shown in Figure 9.
FIG. 10 shows the reaction force acting on the pivot shaft 5. Also,
FIG. 11 shows the reaction force acting on the shaft 3, FIG. 12 shows the absolute value of the reaction force acting on the pivot shaft 5, and FIG. 13 shows the absolute value of the reaction force acting on the shaft 3.

Note that these data were obtained as a result of computer analysis.

By the way, when the reaction forces acting on the rotation axis 5 that occur during forward and reverse rotation are combined, the reaction forces in the Y-axis direction and the Z-axis direction cancel each other out, and only the reaction force in the X-axis direction is combined, resulting in the 14th rotation.
The graph shown in the figure is obtained.

This can be considered to be a combination of +108 and 9 reaction forces when the rotation angle is 0°, and -58 reaction forces when the rotation angle is 180°. In other words, the fourteenth
This means that a thrust force in the X-axis direction shown in the figure is generated. Specifically, this refers to a case in which, for example, two sets of links 1 and 2 are rotated forward and reverse in the same phase and synchronously around the pivot shaft 5, respectively.

Furthermore, when the graph of FIG. 14 is synthesized with a phase difference of 180°, the graph shown in FIG. 15 is obtained. In FIG. 15, A is a composite of /kl and A' having a phase difference of 180°. This can be thought of as a combined reaction force (thrust) of +50 to 9 acting in the X-axis direction at a period of 180 degrees during the rotation of the links 1 and 2. Specifically, for example, four sets of links 1 and 2 are installed around the pivot shaft 5, and two sets each of 18
This means the case of forward and reverse rotation with a phase difference of 0°.

16 to 21 show the results obtained when the device shown in FIG. 1 is used for normal rotation at a rotation speed of 120 rpm. Figure 18 is Figure 4, Figure 19 is Figure 5, Figure 20 is Figure 6, and Figure 2.
1 corresponds to FIG. 7.

Figures 22 to 27 show the device shown in Figure 1;
The length of link 2 is 125 mm, and the rotation speed is 60 rPm.
Figure 22 shows the results when normal rotation is performed.
Figure 3 is Figure 3, Figure 24 is Figure 4, Figure 25 is Figure 5,
FIG. 26 corresponds to FIG. 6, and FIG. 27 corresponds to FIG. 7.

28 to 33 similarly show the results when the length of the second link 2 is 250 m [other conditions are the same], and FIG. 28 is the result of FIG. 2, and FIG. Figures 3 and 30 are Figure 4, and Figure 31 is Figure 5.

FIG. 32 corresponds to FIG. 6, and FIG. 33 corresponds to FIG. 7.

34 to 39 similarly show the results when the length of the second link 2 is 750+o+ (other conditions being the same), and FIG. 34 is the result of FIG. 2, and FIG. Figure, No. 36
The figure is Fig. 4, and Fig. 37 is Fig. 5.

FIG. 38 corresponds to FIG. 6, and FIG. 39 corresponds to FIG. 7.

40 to 46 similarly show the results when the length of the second link 2 is set to 50 mm (other conditions being the same), is Figure 3, Figures 42 and 43 are Figure 4, Figure 44 is Figure 5, Figure 45 is Figure 6.
46 corresponds to FIG. 7.

Next, the present invention will be explained in detail.

FIGS. 47 to 51 show a first embodiment, and the first embodiment shown in FIG.
This is to obtain the thrust shown in Figure 4. That is, the casing 10 is divided into upper and lower halves by the partition wall 11, links 20 and 2↓ are installed in the upper chamber 12, and the lower chamber 13 has the same structure, and the links 20 and 21 of the upper chamber 12 are Turn, lower chamber 1
The third links 20°, . . . , 21 are driven in reverse.

Specifically, the first link 20 is fixed to one end of a pivot shaft 22, and the pivot shaft 22 is rotatably mounted on a sleeve 35 attached to the partition wall 11. A sprocket 23 fixed to the other end of the pivot shaft 22 is connected via a chain 24 to a sprocket 25a provided on the output side of a bevel gear mechanism 25. The input side of the bevel gear mechanism 25 is connected to a motor 26, which rotates the upper chamber 2 and the lower chamber 13 in the forward and reverse directions.

The second link 21 has a weight 27 attached to its tip, and is connected to the end of the first link 20 by a shaft 28. This shaft 28 is rotatable with respect to the first link 20 and fixed with respect to the second link 21. Further, a sprocket 29 fixed to the shaft 28 is connected to another sprocket 31 via a chain 30. sprocket 31
is rotatably mounted on a shaft 33 provided on the first link 20, and a spur gear 32 provided integrally with this sprocket 31 meshes with a spur gear 34 fixed to the sleeve 35,
The gear ratio between the two is 1:1.

In the above configuration, the rotational driving force of the motor 26 is divided by the bevel gear mechanism 25 into a forward rotation direction on the upper chamber 12 side and a reverse rotation direction on the lower chamber 13 side.
The first link 20 is rotated forward and reverse at the same speed via the pivot shaft '22. Further, in response to the rotation of the first link 20, the spur gear 32 rotates around the spur gear 34, and the sprocket 31. Chain 30. Sprocket 29. The first link 21 rotates via the shaft 28. This rotation is caused by the spur gear 32
Since the gear ratio of ゜34 is 1=1, the first link 20
One rotation corresponds to one rotation of .

As a result, the resultant reaction force shown in FIG. 14 is generated on the shaft 22, and a vibrating thrust in the X-axis direction (horizontal direction 9) is obtained.

On the other hand, FIGS. 52 to 54 show a second embodiment, which is used to obtain the thrust shown in FIG. 15 above.

That is, the first embodiment is configured in two stages,
Upper section 40. The lower part 41 is driven to rotate with a rotational phase difference of 180°. Of course, the upper chamber 12 of the upper section 40
．． In the lower chamber 13, the first link 20 and the second link 21 are in a forward and reverse rotational relationship, respectively. Further, the upper chamber 12 of the lower section 41. In the lower chamber 13, there is a relationship of reverse rotation and forward rotation.

According to this, thrust in one direction (forward only) of the X axis shown in FIG. 15 above can be obtained.

FIGS. 55 and 56 show a third embodiment, which is intended to obtain a composite reaction force (thrust) similar to that of the second embodiment. However, the structure is similar to the first embodiment, and the difference is that the first link 20.20 of the upper and lower chambers 12.13 in the first embodiment is replaced with one first link 20a, and this first The pivot shaft 22 is fixed at the center of the link 20a, and the rotation direction of the first link 20a is normal rotation S. The second link 21a is rotated in the normal direction.

The rotational direction of 21b is also normal rotation. Note that the driving force transmission mechanism is the same, and the spur gear 34 has two spur gears 32.
．． 32 mesh.

Here, the reaction forces in the X-axis and Y-axis directions and the combined reaction force in the X-axis direction acting on the pivot shaft 22 in the second embodiment are expressed as
This is shown in Figures 61 to 61. In each figure, A/ and A'' are reaction forces in the X-axis direction having a phase difference of 180°, and A is a composite of these reaction forces.

However, Figure 57 is under the conditions in Figure 2 above, Figure 58 is under the conditions in Figure 212, Figure 59 is under the conditions in Figure 28, and Figure 60 is under the conditions in Figure 34. , FIG. 4 shows data under the conditions shown in FIG.

Then, the resultant reaction force A shown in FIGS. 57 to 61 is 1
By combining with a phase difference of 80°, it is possible to obtain a combined reaction force only in the X-axis direction having a substantially constant value as shown in FIG. 62.

In addition, in the third embodiment, since only forward rotation occurs, a couple of forces in the reverse direction is generated throughout.

Therefore, as a method to eliminate the drawback of this couple generation, the fourth
An example is shown. The fourth embodiment is shown in FIG. 63.

As shown in FIG.
a, rotate the second links 21a and 21b in the normal direction, and rotate the first link of the lower chamber 13.
Link 20a, second link 21a.

21b is reversed.

As a result, the above-mentioned couple is eliminated, and the resultant reaction force in the X-axis direction acting on the pivot shaft 22 can obtain a substantially constant value, as shown in FIG. 62.

FIG. 65 shows a fifth embodiment, in which four first links 20 are integrally provided at 90° intervals and fixed to a shaft 22 at the center to drive forward rotation, while each second link 21 also rotates forward. It is something that is driven.

According to this, although the force couple is not eliminated, the resultant reaction force in the X-axis direction shown in FIG. 15 can be obtained.

FIG. 66 shows a sixth embodiment, in which a two-link structure consisting of a first link 20 and a second link 21 is provided on the same plane 40, one set on each side, and the left side rotates normally.

This is to reverse the right side.

With this, the resultant reaction force in the X-axis direction is doubled, and by making the Y-axis coincide, the couple can also be eliminated.

Furthermore, FIG. 67 shows a seventh embodiment, in which the casing 10
The center of the first link 21a is rotatably mounted on a pivot shaft 22 fixed to
A and the second link 21a, 2 directly connected to this motor 2 stations
The weights 27, 27 are connected to the motor 26a.
It is directly rotationally driven. Further, a sprocket 41 fixed to the output shaft of the motor 26a and a sprocket 43 rotatably attached to the first link 20a are connected by a chain 42, and a gear 44 fixed coaxially with the sprocket 43 is connected to the rotation axis. It meshes with a gear 45 fixed to 22. Therefore, the driving force of the motor 26a is
2. It is transmitted to the gear 44 via the sprocket 43, and the gear 44 moves around the fixed gear 45, thereby rotating the first link 20a.

FIG. 68 shows an eighth embodiment, in which a dedicated motor 26b is provided to rotate the first link 20a, and a motor 26a is provided to rotate the second links 21a and 21b.
It is the same as that shown in FIG. 67 in that it is provided with .

FIG. 69 shows a ninth embodiment, in which the driving force of the motor 26 is transmitted to the rotating shaft 22 via the bevel gear mechanism 50, and the rotation of the rotating shaft 22 is transferred to the bevel gear mechanism 51 and the first link 20a.
The second link 21a is connected to the second link 21a via bevel gear mechanisms 52a and 52b provided at both ends of the link.

21h.

FIG. 70 shows a tenth embodiment, in which the first link 20a is provided in two stages, a motor 26b is directly connected to the pivot shaft 22, and a planetary gear 54 is meshed with a gear 53 fixed to the pivot shaft 22. Sprocket 55 coaxial with 54
and the sprocket 57 fixed to the shaft 58 are connected to the chain 56.
It is connected via.

FIG. 71 shows an eleventh embodiment, in which a motor 2 is mounted on the pivot shaft 22.
6b, a cylinder 60.60 is rotatably installed at the rear end of the first link 20H, and the tip of the piston rod 61 of the cylinder 60 is fixed to the shaft 62.
It is connected to. In this one, the first link 20
The piston rod 61 reciprocates once in conjunction with one rotation of a,
The second links 21a and 21b rotate once around the shaft 62.

FIGS. 72 and 73 show a twelfth embodiment, in which an inner ring body 70 and an outer ring body 71 are integrally provided in the casing lO and are rotatable by a motor 26b, and both ring bodies 70.7
A weight 27 is fixed to the tip of the piston rod 73 of eight air cylinders 72 provided in the radial direction between the two. The pivot shaft is located at the center of the ring body 70, and the hole 82 formed in the side wall of the air inlet 1, 81 is located at the center of the ring body 70.
The hole 83 can communicate with the rear chamber of the cylinder 72, and the hole 83 can communicate with the front chamber of the cylinder 72. -Tt of the disk body 85 that surrounds the pivot shaft 80 and supports the rear end of the cylinder 72, 86 can communicate with the rear chamber of the cylinder 72;
can communicate with the anterior chamber and the posterior chamber, respectively.

Open the vestibule to the atmosphere. The above holes 82, 83, 86° 87
are ring bodies 70, 71, cylinder 72. It can be opened and closed according to the rotation of the disk body 85, and when each cylinder 72 is in the position (5) as shown in FIG.
communicates with the rear chamber of the cylinder 72, the hole 87 communicates with the front chamber of the cylinder 72, and the weight 27 moves back together with the piston rod 73.

When the weight 27 rotates by 45 degrees and reaches the position (B), the weight 27 completely retreats, and continues to rotate 900 times to the 0 position. (At position q, the hole 82 communicates with the front chamber of the cylinder 72, and the hole 86 communicates with the rear chamber of the cylinder 72,
The weight 27 moves forward together with the piston door 3. 45
When the weight 27 rotates through 0° and reaches the 0 position, the weight 27 moves forward completely, and then rotates 180° to the position (~).

That is, in this embodiment, each weight 27 has (
It moves backward between ~ (B) and moves forward between (C) and (D). In this case, the angular velocity is constant, but the radius of gyration of the weight 27 decreases between (to) and β) and increases between (C) and (D). Therefore, a composite reaction force (thrust) in the direction of the arrow X is generated on the rotation axis 80.

Incidentally, if these are stacked one on top of the other to form a two-stage structure and rotated forward and backward, the couple generated at the pivot shaft 80 can be removed.

FIGS. 74 and 75 show a thirteenth embodiment, in which eight links 9o each having a weight 27 at the tip are rotatably mounted on a pivot shaft 92 fixed at the center of the casing 10, while The pivot shaft 92 is a cam plate 9 provided at a certain eccentric position.
The pins 91 protruding from the link 90 are engaged with the long holes 96 of the cam plate 95, and eight long holes 96 are formed radially from the center of the cam plate 95 at equal intervals. Also, the cam plate 9
The output shaft of a motor 26b'' is connected to the center of the motor 26b''.

Therefore, when the motor 26b is rotated in the normal direction, the link 90 rotates clockwise in FIG. 74 about the pivot shaft 92 via the pin 91 which is restrained by the elongated hole 96 of the cam plate 95. At this time, since the cam plate 95 and the link 90 are eccentric, the pin 91 moves back and forth within the elongated hole 96, and when it moves outward, that is, the rotation from the 4th position to the (to) position. During the movement, the angular velocity increases gradually, and when moving inward, that is, during rotation from position (B) to position (to), the angular velocity gradually decreases. Weight 27. The angular velocity of the link 90 is minimum at the position (to) and maximum at the position C), but the turning radius is constant, and the turning axis 92 has an arrow X.
A resultant reaction force (thrust) in the direction is generated.

FIG. 76 and FIG. 77 show the fourteenth embodiment, and the thirteenth embodiment shown in FIG.
Basically the same as in the embodiment, the turning radius is kept constant and the angular velocity is varied. That is, a link 102 having a weight 27 at its tip is rotatably attached to the periphery of a flange 101 fixed to a pivot shaft 100 provided at the center of the casing 10, while the link 102 is at a fixed eccentric position with respect to the pivot shaft 100. The pin 106 of the cam plate 105 provided in the link 102 is inserted into the long hole 10 of the link 102.
Eight pins 106 are protruded from the center of the cam plate 105 at the same radius and at equal intervals. Further, the cam plate 105 and the rotating shaft 100 each have a motor 2.
6b and 26c are directly connected.

Therefore, when the motors 26a and 26b are rotated normally at the same rotation speed, the link 102 rotates clockwise in FIG. 76 while the pin 106 moves back and forth within the elongated hole 103. When the pin 106 moves outward within the elongated hole 103, i.e. (
During the rotation from the position 0 to the position 0, the angular velocity gradually increases and moves inward, i.e. from the 0 position to the position 0.
The angular velocity gradually decreases during the rotation to the position ( ). Weight 27. The angular velocity of the link 102 is the minimum at the position (to) and the maximum at the position C), but the turning radius is constant, and a resultant reaction force (thrust) in the direction of the arrow X is generated at the turning axis 100.

As is clear from the above description, in both this embodiment and the thirteenth embodiment, according to the present invention, a weight that can be restrained and rotated about a rotation axis is controlled to have a radius of rotation and an angular velocity for each rotation. With a simple configuration of changing the thrust force shown in Figs. 14, 15, 57 to 62, it is possible to generate the thrust shown in Figs. can.

And such propulsion motors can be used both on land and at sea.

It can be widely applied as a propulsion motor for moving objects on ice, in navigation, and in space.

Of course, the propulsion motor according to the present invention is not limited to the above embodiments, but is within the scope of the gist thereof.

can be changed in various ways.

[Brief explanation of drawings]

1 to 46 are detailed explanations of the present invention, in which FIG. 1 is a plan view of the link mechanism and FIG. 2 is a plan view of the link mechanism. FIG. 8, FIG. 16, FIG. 22, FIG. 28, FIG. 34, and FIG. 40 are schematic diagrams of movement, and FIG. 3 and FIG. 9. FIG. 17, FIG. 23, FIG. 29, FIG. 35, and FIG. 41 are graphs showing the displacement of the weight, and FIGS. 4 to 7. Fig. 10 - Fig. 13, Fig. 18 - Fig. 21, Fig. 24 -
Fig. 27, Fig. 30 - Fig. 33, Fig. 36 - Fig. 39,
42 to 46 are graphs showing the reaction force, and FIGS. 14 and 15 are graphs showing the combined reaction force. 47 to 51 show the first embodiment, FIG. 47 and FIG. 49 are plan views, and FIG. 48 is a plan view. FIG. 50 is a sectional view, and FIG. 51 is a partially sectional plan view showing the state of movement. 52 to 54 show a second embodiment, in which FIG. 52 is a sectional view and FIG. 53 is a cross-sectional view. FIG. 54 is a partially sectional plan view. 55 and 56 show the third embodiment, FIG. 55 is a plan view, and FIG. 56 is a cross-sectional view. 8 FIGS. 57 to 62 are graphs showing the combined reaction force. 63 and 64 show the fourth embodiment, with FIG. 63 being a plan view and FIG. 64 being a sectional view. 65th
The figure is a plan view showing the fifth embodiment, FIG. 66 is a plan view showing the sixth embodiment, FIG. 67 is a sectional view showing the seventh embodiment, and FIG.
8 is a sectional view showing the eighth embodiment, FIG. 69 is a sectional view showing the ninth embodiment, FIG. 70 is a sectional view showing the tenth embodiment, and FIG. 71 is a sectional view showing the eleventh embodiment. FIG. 72nd
The figure is a plan view showing the twelfth embodiment, and FIG. 73 is a sectional view thereof. Fig. 74 is a plan view showing the 13th embodiment; Fig. 75 is a plan view showing the thirteenth embodiment;
The figure is a sectional view thereof. FIG. 76 is a plan view showing the fourteenth embodiment, and FIG. 77 is a cross-sectional view thereof. 1.20,20a...first link, 2,21°21a
, 211) - second link, 90, 102... link,
4,27... Weight, 5,22,80,92°100-
...Swivel axis, 26.26a, 26b, 26C...
Motor, 72...Air cylinder. Patent Applicant Osaka Fuji Kogyo Co., Ltd. Agent Patent Attorney Seibakuho and 2 others Engraving of the drawings (no changes to the content) Figure 3 Figure 4 @ Figure 5 Figure 6 Figure 7 Figure 9 m10 Figure 11 -wo, oo----------------'
-------1 Figure 12 100 "-----] Figure 11 gono, - 轡一一---销---------Aichi---
--□■---ko1
(( Fig. 14 + 1 1 Heel solution -- Fig. 15 臘1ht-□ 1 Fig. 20 Fig. 21 Fig. 22 1" Fig. 23 Fig. 25 Fig. 27 Fig. 28 ↑ Fig. 29 Fig. 30 40.0oV
-------m=--1 Fig. 31 Fig. 32 40.001-- -------1-
---------------K1 Fig. 35 2.0Or-----------1 Fig. 36 100.00. −−−−−−−−−−−−−−−−−−
−−−−−−−−−−−−−−−−−−−m−1oo
, ooL-----1------------J 3rd
71!1 Figure 38 Figure 39 @O, 0Ch------
--------*@4o'5M +・ Fig. 41 1+, oot------------j--1--1111----Fig. 44 20. 0(h------------1---------
−〜−−−−−−−１−−−−−−−１醗■ Figure 45 +S, OO−−−−−−−−−−−−−−−−−−−−
−−−−−−−−−−−−−−−−−−−( Figure 46 Procedural amendment (method) June 10, 1980 Director General of the Patent Office Mr.■, Indication of the case 1988 Patent application No. 17026 2 Name of the invention Propulsion motor 3 Relationship with the case of the person making the amendment Patent applicant address 1-21 Jokoji Nishinomachi, Amagasaki City, Hyogo Prefecture Name
Osaka Fuji Industries Co., Ltd. Representative Oshima Fube 4, Agent (1) I have amended the document (power of attorney) certifying the power of representation as shown in the attached document. (2) The drawings (all drawings) will be corrected as shown in the attached sheet. Please note that this amendment is to clearly draw the photocopied drawing attached at the time of application using dark ink, and there is no content amendment.

Claims (1)

[Claims] 1. A weight that can be rotated while being restrained around a rotation axis is changed at least either the radius of rotation or the angular velocity each time it rotates, and the centrifugal force in one direction is changed from the centrifugal force in the opposite direction. A propulsion motor that is characterized by being more like a dog. 2. At least two sets of identical devices equipped with weights that can be restrained and rotated around a rotation axis are provided, and each weight is rotated in opposite directions in synchronization with the same radius of rotation and angular velocity. A propulsion motor according to claim 1. 3. A patent claim characterized in that at least two sets of identical devices each having a weight that can be restrained and rotated around a rotation axis are provided, and each weight is rotated with the only difference being that the rotation period is shifted by π. The propulsion motor according to item 1.