Compressor assembly and refrigeration appliance
By optimizing the design of compressor components to meet specific parameter relationships, the problem of worsening liquid receiver vibration was solved, the vibration response of the liquid receiver was optimized, dynamic load and noise were reduced, and the reliability and noise performance of the compressor were improved.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- GUANGDONG MEIZHI COMPRESSOR
- Filing Date
- 2026-04-27
- Publication Date
- 2026-06-12
Smart Images
Figure CN122191083A_ABST
Abstract
Description
Technical Field
[0001] This invention relates to the field of compressor technology, and in particular to a compressor assembly and refrigeration equipment. Background Technology
[0002] In roller compressors, vanes are rotatably connected to the hinge holes of the rollers to coordinate the reciprocating motion of the vanes within the working chamber with the rotation of the rollers. However, the inertial torque h of the rollers during reciprocating motion is transmitted to the housing through the vanes and cylinder, generating a periodic vibration response and causing a deterioration in the fundamental frequency vibration of the reservoir. This deterioration of vibration may not only cause reliability issues such as reservoir structural fatigue and weld cracking, but may also further aggravate system noise, affecting the overall operational stability and user experience. Summary of the Invention
[0003] The main objective of this invention is to provide a compressor assembly and refrigeration equipment designed to optimize the vibration response characteristics of a liquid receiver.
[0004] To achieve the above objectives, the compressor assembly proposed in this invention includes a compressor and a liquid receiver connected to the compressor, wherein the axial direction of the liquid receiver is arranged parallel to the axial direction of the compressor; The compressor includes: The housing has multiple mounting holes at its bottom for mounting foot pads; A cylinder has a working chamber inside, and a sliding vane groove is also provided on the cylinder, which is connected to the working chamber; A crankshaft is rotatably disposed within the working cavity, and the crankshaft is provided with an eccentric portion; A roller, rotatably fitted onto the eccentric portion, the roller having a hinge hole; and A slider is reciprocally inserted into the slider groove, and one end of the slider is rotatably engaged with the hinge hole; The compressor assembly satisfies: ; Wherein, m is the mass of the liquid reservoir; v is the displacement of the compressor; R1 is the distance between the central axis of the liquid reservoir and the central axis of the compressor; f is the operating frequency of the compressor; R2 is the center distance between the mounting hole and the housing; I is the moment of inertia of the compressor assembly; and s is the ratio of the operating frequency f of the compressor to the first natural frequency of the liquid reservoir 20.
[0005] In one embodiment, the mass m of the liquid reservoir and the displacement v of the compressor satisfy: .
[0006] In one embodiment, the outer radius r1 of the reservoir satisfies 15mm < r1 < 55mm, and the inner radius r2 of the reservoir satisfies the relationship: 10mm < r2 < 50mm.
[0007] In one embodiment, the mass m, outer radius r1, inner radius r2, and R1 of the reservoir satisfy the following: .
[0008] In one embodiment, the operating frequency f of the compressor satisfies: 0 < f < 300 Hz.
[0009] In one embodiment, the slider includes a hinge joint, a neck, and a main body distributed sequentially along the length direction. The main body is reciprocally inserted into the slider groove. The hinge joint has an orthographic projection along the axial direction. The outer periphery of the orthographic projection includes a first arc segment, a third arc segment, and a transition segment connecting the first arc segment and the third arc segment. Wherein, the first arc segment and the third arc segment are located on the same reference base circle, and the reference base circle and the transition segment enclose and form a gap; The hinge hole includes a rotating fitting part and a connecting part. The connecting part passes through the outer periphery of the roller and is connected to the rotating fitting part. The hinge joint is rotatably disposed on the rotating fitting part.
[0010] In one embodiment, the transition segment is configured as an arc.
[0011] In one embodiment, the center O2 of the transition segment is located between the center O1 of the reference base circle and the main body, and the radius of the transition segment is greater than the radius of the reference base circle.
[0012] In one embodiment, the angle β between the two lines connecting the two ends of the third arc segment to the center of the reference base circle is 45 degrees to 120 degrees.
[0013] In one embodiment, the neck is located in the connecting portion.
[0014] In one embodiment, the width t of the connecting portion, the diameter D1 of the reference base circle, and the thickness d1 of the neck satisfy: 0.20 < (t-d1) / D1.
[0015] The present invention also proposes a refrigeration device, which includes the aforementioned compressor assembly.
[0016] In the technical solution of this invention, by limiting the conditions under which the compressor components satisfy inequalities, quantitative constraints are achieved on the vibration transmission path of the compressor and the dynamic response it induces on the liquid receiver, thereby effectively optimizing the vibration response characteristics of the liquid receiver. This significantly reduces the dynamic load borne by the liquid receiver, greatly delaying the risk of failure such as structural fatigue and weld cracking caused by alternating stress; simultaneously, the suppression of vibration energy directly reduces structural radiated noise, improving the noise performance of the compressor components. Attached Figure Description
[0017] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.
[0018] Figure 1 A schematic diagram of a compressor assembly according to an embodiment of the present invention; Figure 2 This is a schematic diagram of the structure of a compressor assembly provided by the present invention from another perspective; Figure 3 A schematic cross-sectional view of an embodiment of the compressor in the compressor assembly provided by the present invention; Figure 4 for Figure 3 A magnified view of a section at point A in the middle; Figure 5 A partial structural schematic diagram of the compressor rollers in a compressor assembly provided by the present invention; Figure 6 This is a partial structural schematic diagram of an embodiment of the compressor vane in the compressor assembly provided by the present invention.
[0019] Explanation of icon numbers: 10. Compressor; 11. Housing; 12. Foot pads; 13. Mounting holes; 20. Liquid receiver; 110. Cylinder; 111. Working chamber; 112. Vane groove; 120. Crankshaft; 200. Roller; 210. Hinge hole; 211. Rotating fit part; 212. Connecting part; 300, Slider; 301, Reference base circle; 302, Notch; 310, Main body; 320, Hinge joint; 321, First arc segment; 322, Third arc segment; 323, Transition segment; 330, Neck.
[0020] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation
[0021] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.
[0022] It should be noted that if the embodiments of the present invention involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.
[0023] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.
[0024] This invention proposes a compressor assembly.
[0025] Please see Figures 1 to 4 In one embodiment of the present invention, the compressor assembly includes a compressor 10 and a liquid reservoir 20 connected to the compressor 10, wherein the axial direction of the liquid reservoir 20 is arranged parallel to the axial direction of the compressor 10. The compressor 10 includes: The housing 11 has a plurality of mounting holes 13 at its bottom for mounting foot pads 12; A cylinder 110 is disposed inside the housing 11. The cylinder 110 has a working chamber 111 and a sliding vane groove 112, which is connected to the working chamber 111. A crankshaft 120 is rotatably disposed within the working cavity 111, and the crankshaft 120 is provided with an eccentric portion; A roller 200 is rotatably fitted onto the eccentric portion, and the roller 200 is provided with a hinge hole 210; and The slider 300 is reciprocally inserted into the slider groove 112, and one end of the slider 300 is rotatably engaged with the hinge hole 210; The compressor assembly satisfies: ; Where m is the mass of the liquid reservoir 20, in g; v is the displacement of the compressor 10, wherein, for a dual-cylinder or multi-cylinder compressor, v is the sum of the theoretical displacements of each cylinder of the compressor; R1 is the distance between the central axis of the liquid reservoir 20 and the central axis of the compressor 10; f is the operating frequency of the compressor 10; R2 is the center distance between the mounting hole 13 and the housing 11, that is, the distance between the central axis of the mounting hole 13 and the central axis of the housing 12; I represents the moment of inertia of the reservoir 20. This moment of inertia can be obtained by analyzing the mass properties of the reservoir 20 based on a three-dimensional model using computer-aided design software (such as SolidWorks, UG, etc.), or by measuring it experimentally on a physical prototype using the compound pendulum method or torsional pendulum method. s is the ratio of the operating frequency f of the compressor 10 to the first natural frequency of the liquid receiver 20. The first natural frequency of the liquid receiver 20 can be obtained through modal analysis experiments.
[0026] It is understood that the compressor 10 is configured as a roller compressor. When the crankshaft 120 is driven to rotate by the motor, the eccentric part drives the roller 200 to roll eccentrically along the inner wall of the working chamber 111. While the vane 300 moves with the roller 200, it can rotate freely around the hinge point and reciprocate linearly along the vane groove 112. This causes the volume of the working chamber to change periodically with the rotation of the crankshaft 120, thereby sequentially experiencing the three stages of intake, compression and exhaust, so as to realize the continuous intake, compression and exhaust of refrigerant gas.
[0027] The ratio in the above formula has the dimension of acceleration, and physically represents the amplitude of the equivalent vibrational acceleration induced by the inertial excitation of the compressor at the critical part of the liquid receiver. This ratio is limited to 0 to... Within the specified range, quantitative constraints and precise control of the system's dynamic response were achieved.
[0028] The numerator of this ratio comprehensively characterizes the excitation intensity: displacement v and operating frequency f together determine the magnitude of the inertial force, while (2πf) 2This indicates that the excitation is transmitted in the form of acceleration, which increases quadratically with frequency f, highlighting the vibration amplification effect under high-frequency conditions; R1 2 As a lever arm term, it reflects the sensitivity of the installation position of the reservoir 20 to torque transmission; while mass m reflects the weight of the reservoir 20 in the synergistic optimization of mass, stiffness and inertia.
[0029] The denominator of this ratio characterizes the overall vibration stiffness and damping characteristics of the system. Wherein, R2 2 This demonstrates the effectiveness of the foot pad 13's placement in resisting overturning moment; the moment of inertia I reflects the compressor assembly's inertial response capability against high-frequency excitation; [(1-s)] 2 -s 2 This introduces a correction factor for the current operating conditions of the compressor components.
[0030] This inequality enables coupled regulation and global optimization among multiple parameters. It can identify key influencing factors through sensitivity analysis and flexibly adjust different parameters to ensure that the above ratios are within the corresponding range.
[0031] By ensuring that the above ratios meet the corresponding range, the equivalent vibration acceleration of the compressor assembly is much lower than the critical level of fatigue damage in the metal structure, which significantly delays the risk of failure such as structural fatigue and weld cracking caused by alternating stress. At the same time, the suppression of vibration energy directly reduces structural radiated noise and improves the noise performance of the compressor assembly.
[0032] Furthermore, by restricting the ratio to be greater than 0, (1-s) is implicitly limited. 2 -s 2 >0, that is, 1-2s>0, meaning that the operating frequency of compressor 10 must be lower than half of the first natural frequency of liquid receiver 20, so as to ensure that the system always operates in a stable frequency band far away from the resonance region.
[0033] The ratio mentioned above can be 2m / s 2 5m / s 2 8m / s 2 10m / s 2 12m / s 2 14m / s 2 wait.
[0034] In one embodiment, the mass m of the reservoir 20 and the displacement v of the compressor 10 satisfy: This inequality effectively limits the ratio of the compressor 10's displacement v to the receiver 20's mass m, ensuring that the receiver 20 possesses sufficient mass inertia to match the compressor's vibration intensity. This configuration allows the receiver 20 to effectively utilize its inertial force to offset some vibrations and suppress resonance peaks; simultaneously, it optimizes the overall machine's center of gravity distribution, reduces the overturning moment caused by increased displacement, thereby improving the compressor assembly's operational stability, reducing vibration and noise, and extending structural fatigue life.
[0035] In one embodiment, the outer radius r1 of the reservoir 20 satisfies 15mm < r1 < 55mm, and the inner radius r2 of the reservoir 20 satisfies the relationship 10mm < r2 < 50mm. This ensures that the wall thickness of the reservoir 20 is maintained within a suitable range, avoiding both weakening the structural strength due to excessive thinness and material waste or mass redundancy due to excessive thickness. This optimizes manufacturing costs and dynamic performance while ensuring reliability. Specifically, when the mass m of the reservoir 20 is within the range of 500g to 1300g, the combined design of the outer and inner radii further enhances its rotational inertia and stiffness characteristics, which is beneficial for achieving the aforementioned vibration response control objectives.
[0036] In one embodiment, the mass m, outer radius r1, inner radius r2, and R1 of the reservoir 20 satisfy: ; Specifically, the mass m of the reservoir 20 is in g, and the outer radius r1, inner radius r2, and center distance R0 are in mm.
[0037] Where, expression The moment of inertia of the reservoir 20 as it rotates about its own central axis, additional item. This involves translating the moment of inertia from the center of mass of the reservoir 20 to the reference axis of the overall vibration system of the compressor 10. The sum of these two axes characterizes the total moment of inertia of the reservoir 20 relative to the system's vibration reference axis. By limiting this total moment of inertia to the aforementioned range, precise control of the dynamic characteristics of the reservoir 20 is achieved.
[0038] Specifically, the total moment of inertia can be , , Etc. In other embodiments, the total moment of inertia may also be wait.
[0039] In this way, on the one hand, it avoids the liquid receiver 20 being overly sensitive to the excitation of the compressor 10 due to excessively small rotational inertia, thus preventing severe resonance; on the other hand, it also prevents excessive rotational inertia from causing system response lag or structural bulkiness, thereby ensuring that the liquid receiver 20 can maintain good dynamic stability under variable frequency operation conditions and effectively suppressing the vibration amplification effect near the fundamental frequency and its harmonics. At the same time, a reasonable range of rotational inertia helps to improve the impedance matching between the foot pad 12 and the liquid receiver 20, enhance the vibration energy dissipation efficiency, and thus significantly reduce the dynamic load and radiated noise transmitted to the structure, providing a clear quantitative design basis for the lightweight, low-noise, and high reliability of the compressor 10 components.
[0040] In one embodiment, the operating frequency f of the compressor 10 satisfies: 0 < f < 300 Hz. This limits the operating frequency band of the compressor 10 to between the low-order modal response region and the high-frequency noise-sensitive region of conventional mechanical structures, effectively avoiding the risk of severe vibration caused by structural resonance. Within this frequency range, the inertial force of the moving parts inside the compressor increases with the square of the frequency, which is still within a controllable level. This ensures that the compressor 10 has efficient work capacity while avoiding excessive dynamic fatigue loads on the connection between the liquid receiver 20 and the foot pad 13 caused by high-frequency excitation forces. Simultaneously, this frequency band limitation is beneficial for aligning with the relationship between displacement v and mass m in the aforementioned embodiments, ensuring that the vibration absorption characteristics of the liquid receiver 20 can cover the entire operating range of the compressor. This helps suppress structural noise radiation in the mid-to-low frequency range, improving the overall NVH performance and long-term operational reliability of the machine.
[0041] In one embodiment, please refer to Figures 3 to 6 The slider 300 includes a hinge joint 320, a neck 330 and a main body 310 arranged sequentially along the length direction. The main body 310 is reciprocally inserted into the slider groove 112. The hinge joint 320 has an orthographic projection along the axial direction. The outer periphery of the orthographic projection includes a first arc segment 321, a third arc segment 322 and a transition segment 323 connecting the first arc segment 321 and the third arc segment 322. Wherein, the first arc segment 321 and the third arc segment 322 are located on the same reference base circle 301, and the reference base circle 301 and the transition segment 323 enclose and form a notch 302; The hinge hole 210 includes a rotating engagement portion 211 and a communicating portion 212. The communicating portion 212 passes through the outer periphery of the roller 200 and communicates with the rotating engagement portion 211. The hinge joint 320 is rotatably disposed on the rotating engagement portion 211.
[0042] Specifically, by setting the transition section 323, the hinge joint 320 forms a notch, which facilitates its processing and forming. At the same time, the hinge joint 320 and the rotating mating part 211 can form a mating gap, so that the hinge joint 320 can achieve stable and low-friction rotational movement within the rotating mating part 211. Meanwhile, by arranging the first arc segment 321 and the third arc segment 322 on the reference base circle 301, it is ensured that the hinge joint 320 can still maintain good contact with the rotating mating part 211 when it is in the extreme swing position, avoiding local stress concentration or jamming.
[0043] The transition segment 323 can be configured as a single straight line, a single arc, a multi-segment broken line, a multi-segment arc, or a multi-segment mixed line. The inner contour of the rotating mating part 211 can be a continuous arc with the same curvature, and its radius of curvature is slightly larger than that of the reference base circle, so that the first arc segment 321 and the third arc segment 322 fit and conform to the inner wall of the rotating mating part 211. Of course, the rotating mating part 211 can also be provided with arc segments with different curvatures at the position opposite to the reference notch, or a broken line contour formed by connecting multiple straight lines in sequence, as long as the selected configuration does not hinder the normal rotation of the hinge joint 320.
[0044] In one embodiment, the transition segment 323 is configured as an arc, with its center O2 located between the center O1 of the reference base circle 301 and the main body 310. The radius of the transition segment 323 is larger than the radius of the reference base circle 301. Specifically, the larger radius of the transition segment 323 helps to smoothly connect the first arc segment 321 and the third arc segment 322, reducing abrupt changes in contour curvature and thus reducing inertial impact and contact stress during the swinging process of the hinge joint 320. Simultaneously, the center of the transition segment 323 is biased towards one side of the main body 310, making the force flow path of the slider 300 more continuous when under force, which is beneficial to improving structural strength. Thus, while ensuring the degrees of freedom of motion, the stress distribution is optimized, reducing the risk of fretting wear and fatigue cracks.
[0045] Furthermore, in this embodiment, the angle β between the two lines connecting the two ends of the transition segment 323 to the center of the reference base circle 301 is between 45 degrees and 120 degrees. This effectively buffers the oscillating impact while achieving a good balance between structural strength and manufacturing process, ensuring that the slider 300 moves without interference throughout its entire stroke range while maintaining sufficient mechanical strength and stiffness. The angle β can be 45 degrees, 50 degrees, 60 degrees, 70 degrees, 90 degrees, 110 degrees, or 120 degrees. In other embodiments, the angle β can also be 40 degrees, 125 degrees, or 130 degrees.
[0046] In one embodiment, the neck 330 is located in the connecting portion 212. With this configuration, when the slider 300 rotates, the neck 330 region effectively avoids the hole wall structure of the hinge hole 210, avoiding the restriction of the slider 300's swing freedom or the occurrence of local stress concentration due to geometric interference, thereby ensuring the smooth movement of both the slider 300 and the roller 200.
[0047] In one embodiment, please refer to Figure 5 and Figure 6 The width t of the connecting portion 212, the diameter D1 of the reference base circle 301, and the thickness d1 of the neck 322 satisfy: 0.20 < (t-d1) / D1.
[0048] It should be noted that the width t of the connecting part 212 and the thickness d1 of the neck 322 are both dimensions in the same direction, which is roughly parallel to the direction of rotation of the slider 300 relative to the roller 200.
[0049] The difference between the width t of the connecting portion 212 and the thickness d1 of the neck 322, i.e., t-d1, can characterize the clearance between the neck 330 and the connecting portion 212 in the direction of rotation of the slider relative to the roller 200. Based on this, the ratio of this difference to the diameter D1 of the reference base circle 301, i.e., (t-d1) / D1, constitutes a dimensionless parameter that can comprehensively reflect the kinematic compatibility and compactness of the hinge structure. By controlling this ratio within the above range, the structural stiffness of the slider 300 can be maintained while ensuring the degree of freedom of motion.
[0050] Specifically, the ratio can be 0.25, 0.3, 0.35, 0.4, etc. In other embodiments, the ratio can also be 0.15, 0.18, 0.2, etc.
[0051] The present invention also proposes a refrigeration device, which includes a compressor assembly. The specific structure of the compressor assembly is as described in the above embodiments. Since the refrigeration device adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.
[0052] The above description is merely an exemplary embodiment of the present invention and does not limit the scope of protection of the present invention. Any equivalent structural transformations made based on the technical concept of the present invention and the contents of the specification and drawings of the present invention, or direct / indirect applications in other related technical fields, are included within the scope of protection of the present invention.
Claims
1. A compressor assembly, characterized in that, It includes a compressor and a liquid receiver connected to the compressor, wherein the axial direction of the liquid receiver is parallel to the axial direction of the compressor; The compressor includes: The housing has multiple mounting holes at its bottom for mounting foot pads; A cylinder is disposed within the housing, the cylinder having a working chamber, and a sliding vane groove connected to the working chamber. A crankshaft is rotatably disposed within the working cavity, and the crankshaft is provided with an eccentric portion; A roller, rotatably fitted onto the eccentric portion, the roller having a hinge hole; and A slider is reciprocally inserted into the slider groove, and one end of the slider is rotatably engaged with the hinge hole; The compressor assembly satisfies: ； Wherein, m is the mass of the liquid reservoir; v is the displacement of the compressor; R1 is the distance between the central axis of the liquid reservoir and the central axis of the compressor; f is the operating frequency of the compressor; R2 is the center distance between the mounting hole and the housing; I is the moment of inertia of the compressor assembly; and s is the ratio of the operating frequency f of the compressor to the first natural frequency of the liquid reservoir 20.
2. The compressor assembly as claimed in claim 1, characterized in that, The mass m of the liquid reservoir and the displacement v of the compressor satisfy: ; And / or, the outer radius r1 of the reservoir satisfies 15mm < r1 < 55mm, and the inner radius r2 of the reservoir satisfies the relationship: 10mm < r2 < 50mm.
3. The compressor assembly as claimed in claim 1, characterized in that, The mass m, outer radius r1, inner radius r2, and R1 of the liquid reservoir satisfy the following: 。 4. The compressor assembly as claimed in claim 1, characterized in that, The operating frequency f of the compressor satisfies: 0 < f < 300 Hz.
5. The compressor assembly as claimed in claim 1, characterized in that, The slider includes a hinge joint, a neck, and a main body distributed sequentially along the length direction. The main body is reciprocally inserted into the slider groove. The hinge joint has an orthographic projection along the axial direction. The outer periphery of the orthographic projection includes a first arc segment, a third arc segment, and a transition segment connecting the first arc segment and the third arc segment. Wherein, the first arc segment and the third arc segment are located on the same reference base circle, and the reference base circle and the transition segment enclose and form a gap; The hinge hole includes a rotating fitting part and a connecting part. The connecting part passes through the outer periphery of the roller and is connected to the rotating fitting part. The hinge joint is rotatably disposed on the rotating fitting part.
6. The compressor assembly as claimed in claim 5, characterized in that, The transition section is configured as an arc.
7. The compressor assembly as claimed in claim 6, characterized in that, The center O2 of the transition section is located between the center O1 of the reference base circle and the main body, and the radius of the transition section is greater than the radius of the reference base circle.
8. The compressor assembly as claimed in claim 6, characterized in that, The angle β between the two lines connecting the two ends of the third arc segment to the center of the reference base circle is 45 degrees to 120 degrees.
9. The compressor assembly as claimed in claim 5, characterized in that, The neck is located in the connecting portion.
10. The compressor assembly as claimed in claim 5, characterized in that, The width t of the connecting portion, the diameter D1 of the reference base circle, and the thickness d1 of the neck satisfy: 0.20 < (t-d1) / D1.
11. A refrigeration device, characterized in that, Includes the compressor assembly as described in any one of claims 1 to 10.