Hydraulic torque converter and motor vehicle comprising same

Abstract

The present disclosure relates to a torque converter comprising: a cover disposed about an axis of rotation for receiving an input torque; a lock-up clutch comprising a piston disc actuatable in an axial direction between an engaged position and a disengaged position; a torsional damper includes a damper housing and first and second damper spring sets accommodated in the damper housing and spaced apart in a radial direction. The lock-up clutch further comprises one or more transmission plates which are axially arranged between the piston disc and the cover and two ends of which are respectively fixed to the piston disc and the cover, and are used for transmitting torque between the piston disc and the cover, so that the piston disc rotates synchronously with the cover and biases the piston disc towards a disengaged position. The drive plate is arranged radially between the first and second damper spring sets. The invention further relates to a motor vehicle comprising the hydraulic torque converter.

Description

Technical Field

[0001] The present disclosure relates to a hydraulic torque converter and also to a hydraulic torque converter and a motor vehicle comprising the hydraulic torque converter. Background Art

[0002] Generally, a torque converter is provided between the engine and the transmission of an automatic transmission motor vehicle. The torque converter is used to transmit the driving power of the engine to the transmission, and can play the role of transmitting torque and torque conversion. The torque converter may include a cover driven by a driving component on the engine side, a pump wheel connected to the cover in a rotationally fixed manner, a turbine, a torsional vibration damper, a locking clutch, and a wheel hub for outputting torque. The locking clutch includes a piston disc actuated between an engaged position and a disengaged position. The torque converter switches between a fluid transmission mode and a mechanical transmission mode through a locking clutch. In the starting stage of the motor vehicle, the piston disc of the locking clutch is in a disengaged position, and the torque converter works in a fluid transmission mode. At this time, the pump wheel of the torque converter drives the turbine through a fluid (usually oil), and the turbine then directly or indirectly transmits the torque to the wheel hub. After the engine reaches a higher speed, the piston disc of the locking clutch is in an engaged position, and the torque converter switches to a mechanical transmission mode. In mechanical transmission mode, torque is mechanically transmitted from the cover to the wheel hub via the lock-up clutch via the torsion damper and / or other transmission components.

[0003] In order to make the piston disc of the lock-up clutch rotate synchronously with the cover (especially when the piston disc is in the disengaged position), the lock-up clutch may include a transmission plate. The two ends of the transmission plate are respectively fixed to the piston disc and the cover, so that the piston disc and the cover rotate synchronously, avoiding the frustration when the hydraulic torque converter switches the transmission mode.

[0004] However, arranging the transmission plate in the lock-up clutch increases the axial size of the torque converter. This increased axial size of the torque converter is particularly disadvantageous in the case of limited axial space. For example, in the case of a transverse front-wheel drive vehicle, the vehicle engine and the torque converter are arranged side by side in the width direction of the vehicle, and the axial installation space of the torque converter is relatively small, making it difficult to install the torque converter whose axial size is increased due to the arrangement of the transmission plate. Summary of the invention

[0005] Therefore, the present disclosure aims to solve the above-mentioned problems existing in the existing torque converter, and its purpose is to provide a torque converter, wherein the position of the transmission plate of the locking clutch is specifically designed so as not to increase the axial size of the torque converter.

[0006] The objective is achieved by a hydraulic torque converter according to an embodiment of the present disclosure. The hydraulic torque converter comprises: a cover, which is arranged around a rotation axis and is used to receive input torque; a locking clutch, which comprises a piston disc, which can be actuated in an axial direction between an engaged position and a disengaged position; a torsional vibration damper, which comprises a vibration damper housing and a first vibration damper spring group and a second vibration damper spring group which are accommodated in the vibration damper housing and separated in a radial direction. The locking clutch also comprises one or more transmission plates, which are axially arranged between the piston disc and the cover and whose two ends are respectively fixed to the piston disc and the cover, and are used to transmit torque between the piston disc and the cover, so that the piston disc rotates synchronously with the cover and biases the piston disc toward the disengaged position. The transmission plate is radially arranged between the first vibration damper spring group and the second vibration damper spring group.

[0007] In the present disclosure, the torsional vibration damper includes two damping spring groups separated in the radial direction, and the radial position of the transmission plate of the locking clutch is between the first damping spring group and the second damping spring group. Compared with the torsional vibration damper of a single damping spring group, the torsional vibration damper of the two damping spring groups has a better vibration reduction effect. The damping springs in the damping spring group have a certain diameter and are components with a large axial dimension in the torque converter. Radially arranging the transmission plate between the two damping spring groups avoids the overlap of the transmission plate and the damping spring group in the radial direction, and does not cause the axial dimension of the torque converter to increase. In addition, through the above-mentioned structure, the projections of the transmission plate and the damping spring group in the axial direction at least partially overlap, thereby making full use of the space between the two damping spring groups.

[0008] The torque converter according to the present disclosure may also have one or more of the following features alone or in combination.

[0009] According to an embodiment of the present disclosure, the lock-up clutch further includes an intermediate plate axially arranged between the piston plate and the cover, the intermediate plate transmitting torque to the first damping spring group and the second damping spring group of the torsional vibration damper.

[0010] According to one embodiment of the present disclosure, in the engaged position, the cover directly transmits torque to the intermediate plate to drive the intermediate plate to rotate, and the intermediate plate transmits torque to the first damping spring group and the second damping spring group of the torsional vibration damper, and in the disengaged position, the cover does not directly transmit torque to the intermediate plate.

[0011] According to the above configuration, in the lock-up clutch, the piston disc and the cover rotate synchronously through the transmission plate, and the rotation state of the intermediate disc is different according to the position of the piston disc. When the piston disc is in the engaged position, the intermediate disc is driven to rotate by the cover, and the torque is transmitted from the cover to the first damping spring group and the second damping spring group of the torsional vibration damper through the intermediate disc. When the piston disc is in the disengaged position, there is no direct torque transmission between the cover and the intermediate disc, and the torque converter is in the fluid transmission mode at this time.

[0012] According to one embodiment of the present disclosure, the torque converter further includes: a pump wheel, which is arranged around the rotation axis and includes a pump wheel housing fixedly connected to the cover; a turbine, which is arranged axially opposite to the pump wheel around the rotation axis and includes a turbine housing; and an output hub, which is arranged around the rotation axis and fixedly connected to the turbine housing for outputting torque. The damper housing is fixedly connected to the output hub.

[0013] According to the above structure, when the piston disc is in the engaged position, the first damping spring group and the second damping spring group of the torsion damper transmit torque to the damper housing, and then to the output hub. The transmission path of torque from the cover to the output hub is composed of mechanical components, and the torque converter is in a mechanical transmission mode. When the piston disc is in the disengaged position, the torque is transmitted from the cover to the output hub via the pump wheel and the turbine, wherein the pump wheel drives the turbine through the fluid, and the torque converter is in a fluid transmission mode.

[0014] According to an embodiment of the present disclosure, two ends of the transmission plate are riveted to the piston disc and the cover respectively. It should be understood that other feasible connection modes of the transmission plate, the piston disc and the cover are also conceivable.

[0015] According to an embodiment of the present disclosure, one or more through holes are provided on the piston plate, and a riveting tool can pass through the through holes to rivet the transmission plate to the cover.

[0016] According to an embodiment of the present disclosure, the piston disc further includes one or more plugging caps to seal the through hole after riveting is completed, so that the transmission plate will not be exposed in the axial direction.

[0017] According to an embodiment of the present disclosure, the cover is provided with one or more riveting protrusions for riveting the corresponding ends of the transmission sheet to the cover, wherein the positions of the riveting protrusions correspond to the through holes.

[0018] According to one embodiment of the present disclosure, the radial positions of the two ends of the transmission plate are substantially the same.

[0019] According to an embodiment of the present disclosure, the transmission plate has an arc shape when viewed in the axial direction. The arc shape of the transmission plate can prevent the middle portion of the transmission plate from occupying the radial inner space of the locking clutch.

[0020] According to one embodiment of the present disclosure, the center of the arc shape of the transmission plate is located on the rotation axis.

[0021] According to an embodiment of the present disclosure, the transmission plate has a certain rigidity so that when the relative rotation of the piston disc and the cover squeezes the transmission plate, the middle part of the transmission plate will not contact the piston disc or the cover. When transmitting torque, the transmission plate is subjected to a squeezing force or a tensile force in the circumferential direction. When the transmission plate is squeezed, the transmission plate is deformed so that the middle part thereof is arched. When the rigidity of the transmission plate is sufficient, the deformation of the transmission plate is small so that the middle part thereof will not contact the piston disc or the cover.

[0022] According to an embodiment of the present disclosure, the transmission sheet comprises a plurality of stacked elastic sheets. Through the stacked structure, the transmission sheet can be made of materials of standard specifications, thereby reducing production costs while having sufficient rigidity.

[0023] According to an embodiment of the present disclosure, the transmission plate is formed of high carbon spring steel.

[0024] According to one embodiment of the present disclosure, the locking clutch comprises six transmission plates evenly arranged around the rotation axis. It should be understood that other numbers of transmission plates or transmission plates arranged unevenly are also conceivable.

[0025] According to one embodiment of the present disclosure, the first damping spring group includes a plurality of first damping springs, and / or the second damping spring group includes a plurality of second damping springs.

[0026] The present disclosure also relates to a motor vehicle comprising a torque converter as described above. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] The above and other features and advantages of the present disclosure will become more apparent through the following detailed description of exemplary embodiments in conjunction with the accompanying drawings, and the description and drawings are only for illustrative purposes and are not intended to limit the scope of the present disclosure in any way. In the drawings:

[0028] Figure 1 is a partially cutaway schematic diagram of a hydraulic torque converter according to an embodiment of the present disclosure.

[0029] Figure 2 yes Figure 1 The torsional vibration damper and lock-up clutch in the torque converter shown are Figure 1 Partial cross-sectional views taken at different angles.

[0030] Figure 3 is a cross-sectional view of the lock-up clutch in the radial direction, showing the piston disk and the transmission plate.

[0031] Figure 4 It is a side view of the transmission plate.

[0032] Throughout the drawings, the same or similar components are indicated by the same reference numerals. DETAILED DESCRIPTION

[0033] In order to make the objectives, technical solutions and advantages of the embodiments of the present disclosure more clear, the technical solutions of the embodiments of the present disclosure will be clearly and completely described below in conjunction with the drawings of the embodiments of the present disclosure.

[0034] Unless otherwise defined, the technical terms or scientific terms used herein shall have the usual meanings understood by ordinary technicians in the field to which the present disclosure belongs. Similar words such as "one", "an" or "the" used in the patent application specification and claims of the present disclosure do not indicate a quantitative limitation, but rather indicate the presence of at least one. Similar words such as "include" or "comprise" mean that the elements or objects appearing before the word include the elements or objects listed after the word and their equivalents, without excluding other elements or objects. Directions such as "axial", "radial" and "circumferential" are defined relative to the rotation axis X of the torque converter. The axial direction is the direction in which the rotation axis X extends, the radial direction is the direction perpendicular to the rotation axis X, and the circumferential direction is the circumferential direction around the rotation axis X.

[0035] Figure 1 1 is a partially cutaway schematic diagram of a hydraulic torque converter 100 according to an embodiment of the present disclosure. For the sake of clarity, a number of components in the structure of the hydraulic torque converter that are not relevant to understanding the technical solution of the present disclosure have been omitted.

[0036] like Figure 1 As shown, the torque converter 100 includes a cover 1, a lock-up clutch 5, a torsional vibration damper 6, a turbine 3, a pump wheel 2 and an output hub 4. The cover 1 is rotationally driven by a driving component on the engine side of the motor vehicle (such as an engine crankshaft, a dual mass flywheel, etc.) to receive input torque and rotate around a rotation axis X. The pump wheel 2 is arranged around the rotation axis X, and includes a pump wheel housing 21 fixedly connected to the cover 1, for example, by welding. In this way, torque is input into the torque converter through the cover 1 and the pump wheel 2. The turbine 3 is arranged axially opposite to the pump wheel 3 around the rotation axis X, and includes a turbine housing 31. The output hub 4 is arranged around the rotation axis X and fixedly connected to the turbine housing 31 for outputting torque. It should be understood that additional torque transmission components can also be provided between the turbine housing 31 and the output hub 4.

[0037] The lock-up clutch 5 and the torsional vibration damper 6 are located between the turbine 3 and the cover 1 in the axial direction. The lock-up clutch 5 includes a piston disc 51 and an intermediate disc 52 axially arranged between the piston disc 51 and the cover 1. The piston disc 51 can be actuated between an engaged position and a disengaged position in the axial direction. In the engaged position, the piston disc 51 and the cover 1 contact the intermediate disc 52 on both sides of the intermediate disc 52. The contact surface of the intermediate disc 52 with the piston disc 51 and / or the cover 1 can be set as a friction surface, so that the piston disc 51 and / or the cover 1 are in friction contact with the intermediate disc 52. At this time, the cover 1 directly transmits torque to the intermediate disc 52 to drive the intermediate disc 52 to rotate. In the disengaged position, the intermediate disc 52 is out of contact with the piston disc 51 and the cover 1, and the cover 1 no longer directly transmits torque to the intermediate disc 52.

[0038] The torsional vibration damper 6 includes a damper housing 61 and a first damper spring group 62 and a second damper spring group 63 which are accommodated in the damper housing 61 and separated in the radial direction, and the damper housing 61 is fixedly connected to the output hub 4 for outputting torque. It should be understood that an additional torque transmission component may also be provided between the damper housing 61 and the output hub 4. The intermediate plate 52 may be provided with a portion in contact with the first damper spring group 62 and the second damper spring group 63, so that the intermediate plate 52 can transmit torque to the damper housing 61 through the first damper spring group 62 and the second damper spring group 63.

[0039] Based on the position of the piston disc 51, the torque transmission from the cover 1 to the output hub 4 can have two paths. In the fluid transmission mode, the piston disc 51 is in the disengaged position. At this time, the cover 1 and the pump wheel 2 are driven by the driving component on the engine side of the motor vehicle, and the rotation of the pump wheel 2 around the rotation axis X causes the working fluid of the torque converter 100 to flow, drive the turbine 3, and then transmit the torque to the output hub 4 through the turbine housing 31. In the mechanical transmission mode, the piston disc 51 is actuated toward the cover 1 to the engaged position, and the cover 1 directly transmits the torque to the intermediate disc 52, and the intermediate disc 52 transmits the torque to the damper housing 61 through the first damping spring group 62 and the second damping spring group 63, and then transmits it to the output hub 4.

[0040] In order to avoid the sense of frustration when the torque converter switches the transmission mode, the lock-up clutch 5 further includes one or more transmission plates 53. The transmission plate 53 is axially arranged between the piston disc 51 and the cover 1, and its two ends are respectively fixed to the piston disc 51 and the cover 1. In this way, even when the piston disc 51 is in the disengaged position, the transmission plate 53 can transmit torque between the cover 1 and the piston disc 51, so that the piston disc 51 rotates synchronously with the cover 1. In this way, when the torque converter 100 switches from the fluid transmission mode to the mechanical transmission mode, there is no need to accelerate the piston disc 51, so that the power switching is smoother.

[0041] In addition, when the piston disc 51 is in the engaged position, the elastic force of the transmission plate 53 in the axial direction can also bias the piston disc 51 toward the disengaged position. When the hydraulic pressure for actuating the piston disc 51 is removed, the transmission plate 53 can push the piston disc 51 back to the disengaged position, playing the role of a reset member.

[0042] In radial position, reference Figure 1 , the transmission plate 53 is arranged on the radial inner side of the intermediate plate 52, which can avoid interference with the intermediate plate 52. In particular, the transmission plate 53 is arranged radially between the first damping spring group 62 and the second damping spring group 63 of the shock absorber 6. The first and second damping spring groups both have a certain radius, so they have a comparable size in the axial direction. The radial middle part of the first and second damping spring groups 62, 63 forms a "recess" where the size of the hydraulic torque converter 100 in the axial direction is reduced, which can be used to arrange the transmission plate 53. The axial extension range of the transmission plate 53 overlaps with at least a part of the axial extension range of the first and second damping spring groups 62, 63, preferably overlaps mostly or completely. Through this arrangement, the increase in the axial size of the hydraulic torque converter 100 caused by the transmission plate 53 is greatly reduced, which is conducive to compressing the overall axial size of the hydraulic torque converter 100. In the case where the axial size of the hydraulic torque converter is limited, such as a transverse front-wheel drive vehicle, this arrangement is particularly suitable.

[0043] The transmission plate 53 as a whole extends in the circumferential and axial directions, and the radial positions of both ends thereof are substantially the same (e.g. Figure 3 As shown), and connected to the piston disc 51 and the cover 1 by riveting at different circumferential positions. Figure 1 It is a cross-sectional view cut at the circumferential position of the end of the transmission plate 53 riveted to the cover 1, Figure 2 It is a cross-sectional view cut at the circumferential position of the other end of the transmission plate 53 riveted to the piston plate 51. Figure 3 This is a cross-sectional view of the lock-up clutch 5 cut along a plane perpendicular to the rotation axis X at a position close to the cover 1 and observed axially toward the piston plate 51 .

[0044] like Figure 1 As shown, the cover 1 is provided with a rivet protrusion 11 on the side facing the piston disc 51, and the rivet protrusion 11 can be formed by extrusion or stamping. The piston disc 51 can be provided with a through hole 54 aligned with the rivet protrusion 11. When the transmission plate 53 is connected to the cover 1, the riveting tool passes through the through hole 54 and rivets the corresponding end of the transmission plate 53 to the cover 1 through the rivet protrusion 11. In addition, it should be noted that Figure 1 What is shown in FIG. 1 is the deformed riveting protrusion 11 after the riveting operation is completed. It is understandable that the cover 1 may also be provided with no riveting protrusion, and the transmission sheet 53 may be riveted to the cover 1 by rivets.

[0045] After the transmission plate 53 is riveted to the cover 1, the through hole 54 of the piston disc 51 can be blocked by a plug cap 55. The plug cap 55 can be connected to the piston disc 51 by welding or other suitable means.

[0046] The other end of the transmission plate 53 is riveted to the piston plate 51 at approximately the same radial position by means of rivets 56. Figure 2 As shown, the rivet 56 passes through the piston disc 51 and the transmission plate 53 to rivet the two together. Optionally, the piston disc 51 can also be provided with a riveting protrusion like the cover 1, and the transmission plate 53 is riveted to the piston disc 51 through the riveting protrusion.

[0047] The above describes that the piston plate 51 and the drive plate 53 of the cover 1 are connected by riveting. It is understandable that the connection method of the drive plate 53 and the piston plate 51 and / or the cover 1 is not limited to riveting, and welding, bonding or other suitable connection methods are also conceivable.

[0048] Figure 3 The distribution of the transmission plates 53 on the lock-up clutch 5 is shown. As shown in the figure, the lock-up clutch 5 includes six transmission plates 53 uniformly arranged around the rotation axis X. Figure 3 The transmission piece 53 shown extends straight from one end to the other end, that is, the transmission piece 53 has a linear shape. Optionally, the transmission piece 53 may also have an arc shape. This arc shape allows the middle part of the transmission piece 53 to give up the radial inner space, so it is particularly suitable for transmission pieces with a longer length. The center of the arc-shaped transmission piece 53 is preferably located on the rotation axis X, so that it is coaxially arranged with the piston plate 51 and the cover 1.

[0049] When transmitting torque or resetting the piston disc 51, the transmission plate 53 will be deformed, and rely on the elastic force generated by the deformation to transmit torque or reset the piston disc 51. In the case of torque transmission, since the speed difference between the piston disc 51 and the cover 1 can be positive or negative, the relative rotation of the piston disc 51 and the cover 1 may either stretch the transmission plate 52 along the length direction or squeeze the transmission plate 52. When squeezed, the middle portion of the transmission plate 52 is deformed and arches toward the piston disc 51 and the cover 1. The transmission plate 52 has a certain rigidity to reduce the degree of deformation and avoid contact between the middle portion and the piston disc 51 and the cover 1. To this end, the transmission plate 52 can be made of high-carbon spring steel to have sufficient rigidity. The transmission plate 52 can also be composed of a plurality of stacked elastic plates 53a to obtain a higher height than a single elastic plate. Figure 4 In the illustrated embodiment, the transmission sheet 53 is composed of two overlapping elastic sheets 53a.

[0050] An embodiment of the present disclosure also provides a motor vehicle including the above-mentioned torque converter.

[0051] It should be understood that the structures described above and shown in the drawings are merely examples of the present disclosure, which can be replaced by other structures that exhibit the same or similar functions for obtaining the desired end result. In addition, it should be understood that the embodiments described above and shown in the drawings should be regarded as constituting only non-limiting examples of the present disclosure, and that it can be modified in many ways within the scope of the patent claims.

Claims

1. A hydraulic torque converter, characterized in that: The torque converter comprises: A cover (1) arranged about a rotation axis (X) for receiving an input torque; A lock-up clutch (5) comprising a piston disc (51) which can be actuated in an axial direction between an engaged position and a disengaged position; A torsional vibration damper (6) comprising a vibration damper housing (61) and a first vibration damper spring group (62) and a second vibration damper spring group (63) accommodated in the vibration damper housing (61) and separated in a radial direction; The locking clutch (5) further comprises one or more transmission plates (53), which are axially arranged between the piston disc (51) and the cover (1) and have two ends respectively fixed to the piston disc (51) and the cover (1), and are used to transmit torque between the piston disc (51) and the cover (1), so that the piston disc (51) and the cover (1) rotate synchronously, and the piston disc (51) is biased toward the disengaged position, and Wherein, the transmission plate (53) is radially arranged between the first damping spring group (62) and the second damping spring group (63).

2. The torque converter according to claim 1, characterized in that: The lock-up clutch (5) further comprises an intermediate plate (52) arranged axially between the piston plate (51) and the cover (1).

3. The torque converter according to claim 2, characterized in that: In the engaged position, the cover (1) directly transmits torque to the intermediate plate (52) to drive the intermediate plate (52) to rotate, and the intermediate plate (52) transmits torque to the first damping spring group (62) and / or the second damping spring group (63) of the torsional vibration damper (6). In the disengaged position, the cover (1) does not directly transmit torque to the intermediate plate (52).

4. The torque converter according to claim 3, characterized in that: The torque converter further comprises: a pump wheel (2) arranged around the rotation axis (X) and comprising a pump wheel housing (21) fixedly connected to the cover (1); a turbine (3) which is arranged axially opposite to the pump wheel (3) around the rotation axis (X) and comprises a turbine housing (31); and an output hub (4), which is arranged around the rotation axis (X) and fixedly connected to the turbine housing (31) for outputting torque; Wherein, the shock absorber housing (61) is fixedly connected to the output hub (4).

5. The torque converter according to claim 1, characterized in that: Two ends of the transmission plate (53) are riveted to the piston plate (51) and the cover (1) respectively.

6. The torque converter according to claim 5, characterized in that: The piston plate (51) is provided with one or more through holes (54), through which a riveting tool can pass to rivet the transmission plate (53) to the cover (1).

7. The torque converter according to claim 6, characterized in that: The piston disc (51) further comprises one or more plugging caps (55) to seal the through hole (54) after riveting is completed.

8. The hydraulic torque converter according to any one of claims 5 to 7, characterized in that: One or more riveting protrusions (11) are provided on the cover (1) for riveting the corresponding ends of the transmission sheet (53) to the cover (1).

9. The hydraulic torque converter according to any one of claims 1 to 7, characterized in that: The radial positions of the two ends of the transmission plate (53) are substantially the same.

10. The hydraulic torque converter according to any one of claims 1 to 7, characterized in that: When viewed in the axial direction, the transmission plate (53) has an arc shape.

11. The torque converter according to claim 10, characterized in that: The center of the arc shape of the transmission plate (53) is located on the rotation axis (X).

12. The hydraulic torque converter according to any one of claims 1 to 7, characterized in that: The transmission plate (53) has a certain rigidity so that when the piston plate (51) and the cover (1) rotate relative to each other to squeeze the transmission plate (53), the middle part of the transmission plate (53) will not contact the piston plate (51) or the cover (1).

13. The hydraulic torque converter according to any one of claims 1 to 7, characterized in that: The transmission sheet (53) comprises a plurality of stacked elastic sheets (53a).

14. The hydraulic torque converter according to any one of claims 1 to 7, characterized in that: The transmission plate (53) is formed of high carbon spring steel.

15. The hydraulic torque converter according to any one of claims 1 to 7, characterized in that: The locking clutch (5) comprises six transmission plates (53) evenly arranged around the rotation axis (X).

16. The hydraulic torque converter according to any one of claims 1 to 7, characterized in that: The first damping spring group (62) includes a plurality of first damping springs (62a), and / or the second damping spring group (63) includes a plurality of second damping springs (63a).

17. A motor vehicle, characterized in that: It comprises a hydraulic torque converter as claimed in any one of claims 1 to 16.

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