JP2009281482A - Pipe vibration damping structure and pipe vibration damping method - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a pipe vibration damping structure capable of providing the sure vibration damping effect more than a case of only a flexible member, relatively inexpensive in manufacturing cost, capable of absorbing a dimensional tolerance even if there is the dimensional tolerance, restraining a weight increase in a pipe, and superior in space-saving performance and installation-removal performance. <P>SOLUTION: In a vibration damping member 14, a minimum inside diameter dimension L1 of an inside space S is smaller than an outside diameter dimension D of the flexible member 10, and a maximum inside diameter dimension L2 of the inside space S is larger than the outside diameter dimension D of the flexible member 10. Thus, in installation with the flexible member 10, the vibration damping member 14 includes a contact part 17 for contacting with the flexible member 10, and an isolation part 18 positioned between the contact part 18 and itself and not contacting with the flexible member 10. The inside space S of the vibration damping member 14 is defined so that its force becomes a degree that the vibration damping member 14 relatively loosely fastens the flexible member 10, while changing the force generated when the isolation part 18 is deformed in the installation with the flexible member 10, to force for pressing the flexible member 10 by the contact part 17. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  This invention is used, for example, in piping for a refrigeration cycle that constitutes a vehicle air conditioner, and has an effect of suppressing propagation of vibration from one pipe member to the other pipe member via a flexible member in the piping. The present invention relates to a pipe damping structure and a pipe damping method using the pipe damping structure.

  For example, Patent Document 1 discloses piping for a refrigeration cycle of a vehicle, particularly piping connecting a compressor and a condenser and piping connecting a compressor and a heat exchanger mounted in an air conditioning unit in a passenger compartment. And having a flexible pipe made of a flexible material, a first hard pipe connected to one end of the flexible pipe, and a second hard pipe connected to the other end of the flexible pipe This is already known.

  During operation of the vehicle, vibrations of the vehicle itself, vibrations of a fluid such as a refrigerant flowing through the pipes, or vibrations or pulsations transmitted from the pump or compressor to which the pipes are fastened are easily vibrated. However, while it is widely known as shown in the prior art items of Patent Document 1 and Patent Document 2, in recent years, there has been a strong demand for reducing vibration propagation into the vehicle interior.

  In response to this, as shown in Patent Document 2 described above, an annular weight for vibration control is attached to the outer surface of the pipe with a gap, and the cover has a flexible function and covers the weight. A structure for reducing vibration of a pipe having a configuration in which the pipe is provided is already known.

Moreover, as shown in Patent Document 3, for example, a pipe composed of a metal tube having an outer diameter of 16 mm and a flexible hose having a rubber outer shell, a weight is provided on a part of the side along the longitudinal direction of the metal tube. Also, a vibration preventing structure for an automobile pipe having a structure in which the thickness after heat shrinkage is, for example, 5.5 mm and the heat shrinkable tube having a relatively large thickness is covered is already known.
JP 2006-329350 A JP 2002-174290 A JP 2003-343642 A

  However, in the piping vibration reduction structure described in Patent Document 2, there is an annular gap between the inner peripheral surface of the cover and the weight, as viewed from the axial direction of the cover and the weight. There is a problem that it cannot be obtained. In addition, there are other inconveniences such as a new abnormal noise being generated due to the collision of the weight, and piping being damaged by the weight.

  In addition, in the automobile pipe vibration preventing structure described in Patent Document 3 described above, since the heat shrinkable tube is covered on a part of the metal tube, the portion that should have the flexible function becomes relatively hard and flexible. Therefore, there is a problem that vibration is easily propagated to the entire piping.

  In addition, in recent years, there has also been a demand for reduced manufacturing costs, reduced weight after installation, reduced space occupied by the piping structure, and ease of installation and removal of the piping structure in piping structures that have the effect of suppressing vibration propagation. However, the vibration reducing structure for piping described in Patent Document 2 and the vibration preventing structure for piping for automobile described in Patent Document 3 use weights and weights, which increase the weight. It cannot be said that it fully responds to the request.

  Accordingly, the present invention provides a more reliable vibration suppression effect, is relatively inexpensive to manufacture, can absorb even the dimensional tolerance of each component, and increases the weight of the attached object. The purpose of the present invention is to provide a pipe vibration control structure and a pipe vibration control method that are also excellent in space-saving and attachment / removability.

  The piping vibration control structure according to the present invention is flexible and can be bent in any direction and allows fluid to pass through the flexible member, connected to one end in the longitudinal direction of the flexible portion. A pipe comprising at least a first pipe member and a second pipe member connected to the other end in the longitudinal direction of the flexible member, and an elastic body that can be attached to the outer peripheral side of the flexible member. Thus, the damping member has an internal space that is open on both sides, and the damping member has a value of the maximum static frictional force generated between the flexible member and the damping member of 35 to 75 Newtons. The flexible member can be pressed relatively loosely with respect to the flexible member so as to be more preferably 50 Newton to 60 Newton. Those only to be fitted on the seal member (claim 1). That is, the vibration damping member is not limited to the structure having the closed internal space as shown in claim 2 below, but has a notch extending in the axial direction so that it has an arc shape when viewed from the axial direction. However, the present invention is not limited to the structure having a contact portion that contacts the flexible member and a separation portion that does not contact the flexible member, as shown in claim 2 below. All of them are in contact with each other at the time of mounting on the flexible member. However, since they are spiral, they may be gently pressed against the flexible member as compared with the case of a cylindrical body.

  The piping vibration control structure according to the present invention is flexible and can be bent in any direction and allows fluid to pass through the flexible member, connected to one end in the longitudinal direction of the flexible portion. A pipe comprising at least a first pipe member and a second pipe member connected to the other end in the longitudinal direction of the flexible member, and an elastic body that can be attached to the outer peripheral side of the flexible member. The vibration damping member has an inner space that is open on both sides, and the vibration damping member has a minimum inner diameter dimension of the inner space smaller than an outer diameter dimension of the flexible member, and a maximum inner diameter dimension of the inner space. Is set to be larger than the outer diameter dimension of the flexible member, and when assembled with the flexible member, the outer peripheral surface of the flexible member is always One or more contact portions that are in contact with each other, and a separation portion that is located between a plurality of contact portions or between both ends of the one contact portion and does not always contact the outer peripheral surface of the flexible member, and the internal space When the contact portion is assembled to the flexible member, the separation portion is deformed, and the force generated by the deformation is changed to a force by which the contact portion presses the outer peripheral surface of the flexible member inward. The damping member is defined so as to be able to press the flexible member relatively loosely (Claim 2).

  Here, for the vibration damping member, for example, a relatively light material such as foamed EPDM, solid EPDM, foamed rubber, or foamed plastic is used. Further, the number of damping members is not limited to one. The first pipe member and the second pipe member are made of a hard material such as a metal. The force with which the damping member presses the flexible member relatively loosely ensures that the contact portion of the damping member and the outer peripheral surface of the flexible member can be reliably in contact with each other while the damping member is sheathed. The size is such that the flexible member does not become too hard. Examples of the fluid passing through the flexible member and the first and second pipe members include refrigeration cycle refrigerants such as R134a refrigerant, CO2 refrigerant, and other hydrocarbon refrigerants.

  In this way, the vibration damping member presses relatively loosely against the flexible member, so that the first pipe member or the second pipe member is vibrated in a frequency band from 0 to 1000 Hz, and the second When the propagation of this vibration is measured in the pipe member or the first pipe member, the vibration damping member is relatively tight with respect to the flexible member in the frequency band from 200 Hz to 500 Hz, which is likely to cause noise and vibration problems in the vehicle. An experimental result was obtained that the amount of vibration attenuation was larger than when the vibration damping member was attached or when the vibration damping member was not attached to the flexible member.

  And, by adopting such a vibration damping structure for piping, it is possible to use a flexible material with a relatively low specific gravity without using a material with a large specific gravity called a weight or weight as a damping member. Since the formed member is used, even if the damping member is mounted on the outer peripheral side of the flexible member, it is possible to relatively reduce the increase in weight applied to the pipe. The damping member of the pipe member is not damaged. Moreover, since the flexible member does not become too hard even when the damping member is attached to the flexible member, the effect of suppressing vibration propagation provided in the flexible member does not deteriorate. Since it is not necessary to manage the inner diameter dimension of the internal space of the damping member so strictly, the manufacturing cost of the damping member can be suppressed.

  Further, in order to ensure that the amount of vibration attenuation increases at a frequency from 200 Hz to 500 Hz, the minimum inner diameter dimension and the maximum inner diameter dimension of the internal space are set such that the damping member is the flexible member. It is preferable that the value of the maximum static friction force generated between the flexible member and the damping member is set to be 35 Newtons to 75 Newtons when the pressure is relatively loosely pressed. . As a result, the amount of vibration energy transmitted from one pipe member to the other pipe member is reduced by 50%, and a good vibration damping effect can be obtained.

  Further, in order to increase vibration attenuation at a frequency of 300 Hz or 400 Hz, the minimum inner diameter dimension and the maximum inner diameter dimension of the internal space are set such that the damping member relatively moves the flexible member relative to the flexible member. It is more desirable that the maximum static frictional force generated between the flexible member and the damping member is set to be 50 to 60 Newtons when pressing gently. Thereby, the vibration energy amount transmitted from one pipe member to the other pipe member is reduced by 90%, and a more excellent vibration damping effect can be obtained.

  The pipe damping method according to the present invention is a flexible member that is flexible and can be bent in any direction and allows fluid to pass through the inside, and is connected to one end in the longitudinal direction of the flexible member. A pipe comprising at least a first pipe member and a second pipe member connected to the other end in the longitudinal direction of the flexible member, and an elastic body and disposed on the outer peripheral side of the flexible member. A damping member is used, and for this damping member, the minimum inner diameter of the inner space is smaller than the outer diameter of the flexible member, and the maximum inner diameter of the inner space is smaller than the outer diameter of the flexible member. When it is formed to be large and assembled with the flexible member, a contact portion that always contacts the outer peripheral surface of the flexible member, and the contact Assuming that there is a separation portion that is located between the portions and does not come into contact with the outer peripheral surface of the flexible member, the flexible member and the damping member are assembled, and the contact portion of the damping member is attached to the flexible member It is characterized by being relatively loosely pressed (claim 5). The pipe damping method according to the present invention further includes a caulking member into which the flexible member can be inserted and the first or second pipe member can be inserted, and the flexible member is passed through the damping member. And a step of caulking the flexible member and the first or second pipe member into the caulking member (Claim 6). Thereby, the assembly | attachment operation | work of a damping member and a flexible member is simplified. In this invention as well, the value of the maximum static friction force generated between the flexible member and the damping member is preferably 35 to 75 newtons, and more preferably 50 to 60 newtons. It is.

  On the other hand, in the pipe damping method according to the present invention, the damping member has a cut extending from one end in the axial direction of the damping member toward the other end so that the cut becomes an end face. The thing of the structure expand | deployed to 1 is used, and it may have the process of winding the said damping member around the said flexible member (Claim 7). Thereby, the damping member can be attached to the flexible member after the assembly work of the flexible member and the first and second pipe members.

  As described above, according to these inventions, the vibration damping member presses relatively loosely against the flexible member, so that the frequency from 0 Hz to 1000 Hz is applied to the first pipe member or the second pipe member. When the propagation of this vibration is measured in the second pipe member or the first pipe member, the damping member is made into a flexible member in the frequency range from 200 Hz to 500 Hz which is most likely to occur in a vehicle. On the other hand, the amount of vibration attenuation can be increased as compared to the case where the vibration is attached relatively tightly or the case where the vibration damping member is not attached to the flexible member.

  Moreover, according to these inventions, the vibration damping member is formed of a relatively light material with a relatively low specific gravity without using a material having a relatively large specific gravity called a weight or a weight. Since a thing is used, even if it attaches a damping member to the outer peripheral side of a flexible member, while being able to make the increase in the weight added to piping relatively small, a flexible member and a 1st and 2nd pipe It is possible to prevent the vibration damping member from damaging the member.

  Furthermore, according to these inventions, even when the vibration damping member is mounted on the flexible member, the outer peripheral surface of the flexible member and the vibration damping member do not have an annular gap when viewed from the axial direction of the flexible member. And the damping member do not collide, and no new abnormal noise is generated. Since it is not necessary to manage the inner diameter dimension of the inner peripheral surface in contact with the flexible member of the vibration damping member very strictly, the manufacturing cost of the vibration damping member can be suppressed.

  Furthermore, according to these inventions, the numerical value of the maximum static frictional force generated between the flexible member and the damping member is changed from 35 Newtons to 75 Newtons, so that the pipe member from one pipe member to the other is changed. The amount of vibration energy propagated is reduced by 50%, and a good vibration damping effect can be obtained. Furthermore, according to the present invention, the maximum static frictional force generated between the flexible member and the damping member is set to a value from 50 Newton to 60 Newton, so that it is propagated from one pipe member to the other pipe member. The amount of vibration energy to be reduced is reduced by 90%, and it is possible to obtain a more excellent vibration damping effect.

  And especially according to the invention of Claim 5, simplification of the assembly | attachment operation | work of a damping member and a flexible member can be achieved. In particular, according to the invention described in claim 7, it is possible to attach the vibration damping member to the flexible member even after the assembly work of the flexible member and the first and second pipe members. The work can be simplified.

  Embodiments of the present invention will be described below with reference to the accompanying drawings.

  As an example in which the vibration damping structure for piping according to the present invention is used, a refrigeration cycle 1 of a vehicle air conditioner is shown in FIG. The refrigeration cycle 1 is configured by connecting a compressor 2, a condenser 3, an expansion valve 4, and an evaporator 5 at least by piping. The refrigerant compressed by the compressor 2 and heated to high temperature and pressure is sent to the condenser 3, and the condenser 3 After the high-temperature and high-pressure refrigerant is condensed by releasing heat, the condensed refrigerant is expanded by the expansion valve 4 and further evaporated by the heat absorption from the air flowing in the air conditioning duct 6 by the evaporator 5. The function of returning is known per se. In addition, the kind of refrigerant | coolant includes the refrigerant | coolant for refrigerating cycles, for example, R134a refrigerant | coolant, CO2 refrigerant | coolant, another hydrocarbon type refrigerant | coolant etc., It does not specifically limit. In addition to the compressor 2, the condenser 3, the expansion valve 4, and the evaporator 5, a gas-liquid separator that separates the gas-phase refrigerant and the liquid-phase refrigerant, an internal heat exchanger that exchanges heat between the high-pressure refrigerant and the low-pressure refrigerant, etc. It may have a configuration.

  In this embodiment, the condenser 3 and the compressor 2, and the compressor 2 and the evaporator 5 are connected to each other by pipes 7. As shown in FIG. 2B, these pipes 7 are basically configured to include a first hard pipe 8, a second hard pipe 9, and a flexible member 10.

  Among these, the first hard pipe 8 and the second hard pipe 9 are made of a material having high rigidity such as metal, and are used in places where the layout of piping is relatively severe. ing. As shown in FIG. 4B, the flexible member 10 has a substantially cylindrical shape made of a flexible material such as rubber.

  And the flexible member 10 is connected with the one side edge part along the longitudinal direction of the 1st hard pipe 8 via the cylindrical crimping member 11, and the one end along the longitudinal direction of the 2nd hard pipe The side end is connected to the side caulking member 12 via a cylindrical caulking member 12 and transmits vibration from one of the pipes 8 and 9 to the other (for example, from the hard pipe 9 on the compressor 2 side to the hard pipe 8). In order to attenuate, FIG. 1 shows a state in which a damping member 14 to be described later is mounted, but is used in a state bent at an angle R along the piping layout of the engine room.

  The vibration damping member 14 is disposed on the outer peripheral side with respect to the surface along the axial direction of the flexible member 10, and has a relatively light specific gravity such as foamed EPDM, solid EPDM, foamed rubber, and foamed plastic, and is flexible. Material is used. As shown in FIG. 2, even if the damping member 14 having a thickness of, for example, 3 mm to 5 mm is covered by itself over the entire circumference of the flexible member 10, the thickness is reduced as shown in FIG. 3. For example, a plurality (8 in this embodiment) of 8 mm damping members 14 and 14 may be externally mounted on the flexible member 10.

  When the single damping member 14 of FIG. 2 is used, the caulking members 11 and 12 regulate the axial displacement of the damping member 14 with respect to the flexible member 10, and the two damping members 14 of FIG. 14, the caulking member 11 or 12 and the annular tightening band 15 regulate the axial displacement of the damping member 14 with respect to the flexible member 10. In the case of using a single damping member 14, although not shown, the damping member 14 does not cover the entire range of the flexible member 10, and accordingly, the caulking member 11 or 12 is used by using the fastening band 15. Further, the fastening band 15 may regulate the axial displacement of the damping member 14 with respect to the flexible member 10.

  When the damping member 14 is externally mounted on the flexible member 10, the one or more contact portions 17 that are always in contact with the surface along the axial direction of the flexible member 10 and the plurality of contact portions 17 or one of the contact portions 17. 4 (a). In order to adopt this configuration, the outer portion is located between both ends of the contact portion 17 and has a separation portion 18 that does not contact the surface along the axial direction of the flexible member 10. The internal space S defined by the inner surface facing the side surface along the axial direction of the flexible member 10 also has a regular hexagonal shape as viewed from the axial direction side. The minimum inner diameter dimension L1 shown in FIG. 4 (a) of the internal space S is smaller than the outer diameter dimension D shown in FIG. 4 (b) of the flexible member 10, and in FIG. Maximum inner diameter dimension L shown Is set to be larger than the outer diameter D shown in Figure 4 of the flexible member 10 (b). Here, the damping member 14 has six contact portions 17 and six separation portions 18.

  Thereby, when the damping member 14 is sheathed on the flexible member 10, the separation portion 18 of the damping member 14 is deformed, and the force to return to the original state from the deformation of the separation portion 18 is shown in FIG. ), The surface 17a of the contact portion 17 located on both sides of the separation portion 18 serves as a force for pressing the flexible member 10. Therefore, when the flexible member vibrates, dynamic friction is generated at the contact portion between the flexible member 10 and the contact portion 17 of the damping member 14, and the vibration energy of the flexible member 10 is consumed.

  That is, when the damping member is sheathed on the flexible member with the inner space having a perfect circular shape when viewed from the axial direction and the inner diameter of the inner space being smaller than the outer diameter of the flexible member, If the tolerance dimension control is not strictly controlled for the outer diameter of the flexible member, the damping member is excessively expanded toward the outside in the radial direction, and the pressing force of the damping member on the flexible member is excessive. However, in the vibration damping member 14 according to the present application, these problems are solved.

  The numerical value of the minimum inner diameter dimension L1 shown in FIG. 4A of the internal space S only needs to be smaller than the outer diameter dimension D shown in FIG. 4B of the flexible member 10, and FIG. The numerical value of the maximum inner diameter dimension L2 shown in (a) should be larger than the outer diameter dimension D shown in FIG. 4B of the flexible member 10, and as shown in FIG. Since this dimensional error can be absorbed by changing the shape of the internal space S, it is not necessary to take the dimensional accuracy of the minimum inner diameter L1 and the maximum inner diameter L2 of the damping member 14 very strictly.

  Next, an example of a procedure for mounting the vibration damping member 14 to the flexible member 10 will be described. As shown in FIG. 7, the vibration damping member 14 is formed in a single plate shape by a break line B extending along the axial direction. It is possible to develop a vibration damping member against the flexible member 10 connected to the first hard pipe 8 and the second hard pipe 9 via the caulking member 11 or 12. After the cover 14 is expanded and covered from the side along the radial direction of the flexible member 10, the end surfaces separated by the breaking line B of the damping member 14 are attached by bonding with an adhesive or the like. In addition, it is preferable that the break line B has a position corresponding to the apex of the corner of the separation portion 18 in the damping member 14 as a position of the cut, and thus when the adhesive is applied to the cut, the outer periphery of the flexible member 10 It is possible to prevent the adhesive from adhering to the surface.

  On the other hand, in order to confirm the relationship between tightening and vibration attenuation due to the contact portion 17 of the damping member 14 pressing the side surface along the axial direction of the flexible member 10 at a plurality of locations, the damping member 14 is provided. In the case where the vibration damping member 14 is not tightly tightened with respect to the flexible member 10, the experiment was conducted in three modes: the case where the vibration damping member 14 was tightly tightened with respect to the flexible member 10. In this experiment, as shown by an arrow in FIG. 8A, the second hard pipe 9 is vibrated so that a frequency is generated in a range from 0 to 1000 Hz. This was done by measuring the frequency of each of the hard pipes 9 and comparing them, and authorizing the amount of vibration attenuation in the first hard pipe 8. In FIG. 8A, only the configuration in which the damping member 14 is mounted on the flexible member 10 is shown, but this is for convenience, and the configuration in which the damping member 14 is not mounted on the flexible member 10 is shown. Has also been tested in a similar manner.

  As a result of this experiment, as shown in FIG. 8B, in the configuration in which the damping member 14 is relatively loosely attached to the flexible member 10, the frequency band is 0 compared to the configuration in which the damping member 14 is not attached. Compared with the configuration in which the vibration attenuation amount is large in the entire range from hertz to 1000 hertz and the vibration damping member 14 is relatively tightly attached to the flexible member 10, the vibration of the vehicle itself, the fluid such as the refrigerant flowing through the piping, etc. It is recognized that the amount of vibration attenuation is relatively large in the range from 200 Hz to 500 Hz, which is the main frequency band of vibration or vibration transmitted from pumps and compressors to which such pipes are fastened, and vibration generated by pulsation. It was.

  Accordingly, when attaching the damping member 14 relatively loosely to the flexible member 10, it is confirmed how much force it is appropriate for the contact portion 17 of the damping member 14 to press the flexible member 10. Preferably, the pipe 7 is provided with a flexible member having an outer diameter dimension of 23 mm and a longitudinal dimension of 320 mm. The outer diameter dimension is 38 mm to 40 mm, the inner diameter dimension is 22 mm, the thickness is 7.5 mm to 8 mm, in the longitudinal direction. The second pipe member 9 is bent at an angle of 45 degrees with respect to the first pipe member 8 while the cylindrical vibration-damping member having a dimension of 320 mm is attached, and the second pipe member 9 is bent at an angle of 90 degrees. The maximum static frictional force generated between the vibration damping member and the flexible member by pulling the vibration damping member along the axial direction of the flexible member. In the form of measurement experiments were carried out. It should be noted that the bending angle is set in this way because it is difficult to obtain the vibration damping effect of the flexible member at an angle smaller than 45 degrees, and there are few cases where it is assembled to the vehicle, and at an angle larger than 90 degrees, the flexible structure is flexible. This is because the vibration damping effect of the member is easily obtained and the necessity of the damping member is reduced.

  As a result of an experiment in a configuration in which the flexible member is bent at an angle of 45 degrees with the damping member attached to the entire circumference, as shown in the frame by the two-dot chain line in FIG. 9, the frequency from 200 to 500 hertz In any of the bands, the relative damping amount increased when the damping member pressed the flexible member so that the maximum static frictional force was 35 Newtons to 75 Newtons. In particular, as shown in the frame by the one-dot chain line in FIG. 9, the contact portion of the damping member is made of a flexible member so that the frequency is from 50 Newtons to 60 Newtons at a frequency of 300 Hertz that is most likely to occur in an automobile. When pressing, the amount of vibration attenuation was relatively large.

  Further, even in the result of the experiment in the configuration in which the flexible member is bent at an angle of 90 degrees with the vibration damping member mounted on the entire circumference, as shown in the frame by the two-dot chain line in FIG. In any of the frequency bands up to, when the contact portion of the damping member pressed the flexible member so that the maximum static frictional force was 35 to 75 Newton, the relative attenuation amount was increased. In particular, as shown in the frame by the one-dot chain line in FIG. 10, the contact portion of the vibration damping member is a flexible member so that the frequency is from 50 Newton to 60 Newton at a frequency of 300 Hertz that is most likely to occur in an automobile. When pressing, the amount of vibration attenuation was relatively large.

  However, the numerical values of the minimum inner diameter dimension L1 and the maximum inner diameter dimension L2 of the vibration damping member 14 are set so that when the vibration damping member 14 shown in FIG. Presses the flexible member 10, and a force is generated between the damping member 14 and the flexible member 10 so as to measure a numerical value of 35 Newtons to 75 Newtons, more preferably 50 Newtons to 60 Newtons as the maximum static frictional force. It is required to have a configuration.

  However, the configuration of the damping member 14 is not limited to that shown in FIG. 4A and FIG. 7, and the minimum inner diameter dimension L1 in the inner space S of the damping member 14 is greater than the outer diameter dimension D of the flexible member 10. And the maximum inner diameter dimension L2 is larger than the outer diameter dimension D of the flexible member 10, whereby the damping member 14 has a contact portion 17 and a separation portion 18, and the damping member 14 is attached to the flexible member 10. In this case, the separation portion 18 of the damping member 14 is deformed and the contact portion 17 presses the flexible member 10, whereby the measured value of the maximum static frictional force between the damping material 14 and the flexible member 10 is 35. A numerical value from Newton to 75 Newton, more preferably from 50 Newton to 60 Newton may be measured.

  Hereinafter, modified examples of the damping member 14 will be described with reference to FIGS. 11 to 16. However, the same components as those of the previous damping member 14 are denoted by the same reference numerals, and the description thereof is omitted.

  The damping member 14 shown in FIG. 11 has a regular octagonal outer shape when viewed from the axial direction, and the internal space S also has a regular octagonal shape when viewed from the axial direction. The minimum inner diameter L1 of the internal space S is smaller than the outer diameter D of the flexible member 10, and the maximum inner diameter L2 of the inner space S is larger than the outer diameter D of the flexible member 10. Thereby, when the vibration damping member 14 is assembled with the flexible member 10, the vibration damping member 14 is positioned between the eight contact portions 17 that are always in contact with the outer peripheral surface of the flexible member 10 and the flexible member 10. The eight separation portions 18 that do not contact the outer peripheral surface are provided, and the surface 17 a of the contact portion 17 presses the flexible member 10 relatively loosely by deformation of the separation portion 18. That is, the maximum static frictional force between the damping member 14 and the flexible member 10 is a measured value of 35 Newtons to 75 Newtons, more preferably 50 Newtons to 60 Newtons.

  The damping member 14 shown in FIG. 12 has an outer shape that is a perfect circle when viewed from the axial direction, and an inner space S that is a regular hexagon when viewed from the axial direction. The minimum inner diameter L1 of the internal space S of the damping member 14 is smaller than the outer diameter D of the flexible member 10, and the maximum inner diameter L2 of the inner space S is larger than the outer diameter D of the flexible member 10. Yes. Accordingly, when the vibration damping member 14 is assembled with the flexible member 10, the outer periphery of the flexible member 10 is positioned between the six contact portions 17 that are always in contact with the outer peripheral surface of the flexible member 10 and the contact portion 17. Six separation portions 18 that do not contact the surface are provided, and the surface 17 a of the contact portion 17 presses the flexible member 10 relatively loosely by deformation of the separation portion 18. That is, the maximum static frictional force between the damping member 14 and the flexible member 10 is a measured value of 35 Newtons to 75 Newtons, more preferably 50 Newtons to 60 Newtons.

  The damping member 14 shown in FIG. 13 has an unbalanced shape in which the outer shape is a combination of a perfect circle portion and a projecting portion projecting from the true circle portion in the radial direction when viewed from the axial direction. The internal space S also has an unbalanced shape combining a perfect circle portion and a protruding portion protruding in the radial direction from the true circle portion when viewed from the axial direction, and has a portion that becomes a spring. ing. The maximum inner diameter dimension L2 connecting the protruding portion of the internal space S of the vibration damping member 14 and the center of the perfect circle part is larger than the outer diameter dimension D of the flexible member 10, and the inner diameter dimension of the perfect circle part of the internal space S is also the same. A certain minimum inner diameter dimension L <b> 1 is smaller than the outer diameter dimension D of the flexible member 10. Accordingly, when the vibration damping member 14 is assembled with the flexible member 10, the vibration damping member 14 is positioned between the one contact portion 17 that is always in contact with the outer peripheral surface of the flexible member 10 and both ends of the contact portion 17. 10, one separation portion 18 that does not contact the outer peripheral surface, and due to deformation of the separation portion 18, the surface 17 a of the contact portion 17 presses the flexible member 10 relatively loosely. That is, the maximum static frictional force between the damping member 14 and the flexible member 10 is a measured value of 35 Newtons to 75 Newtons, more preferably 50 Newtons to 60 Newtons.

The damping member 14 shown in FIG. 14 has an outer shape that is a perfect circle when viewed from the axial direction, and an internal space S that is a perfect circle when viewed from the axial direction and the radial direction from the perfect circle. A plurality of projecting portions (12 in this embodiment) projecting radially are combined.
The maximum inner diameter L2 connecting the protruding portion of the internal space S of the vibration damping member 14 and the protruding portion on the opposite side through the center of the perfect circle portion is larger than the outer diameter D of the flexible member 10, and The minimum inner diameter L1 that is also the inner diameter of the perfect circle portion is smaller than the outer diameter D of the flexible member 10. Accordingly, when the vibration damping member 14 is assembled with the flexible member 10, the vibration damping member 14 is positioned between the contact portion 17 and the contact portion 17 that always contacts the outer peripheral surface of the flexible member 10, and the outer periphery of the flexible member 10. There are twelve spaced-apart portions 18 that do not contact the surface, and the deformation of the separated portion 18 causes the surface 17a of the contact portion 17 to press the flexible member 10 relatively loosely. That is, the maximum static frictional force between the damping member 14 and the flexible member 10 is a measured value of 35 Newtons to 75 Newtons, more preferably 50 Newtons to 60 Newtons.

  The damping member 14 shown in FIG. 15 has a plurality of concave portions and convex portions (in this embodiment, eight concave portions and eight convex portions) whose outer shape is along the circumferential direction of the flexible member 10 when viewed from the axial direction. And a plurality of concave and convex portions along the circumferential direction of the flexible member 10 (this embodiment) while the inner space S is similar to the outer shape of the vibration damping member 14 when viewed from the axial direction. Then, 8 concave portions and 8 convex portions) are repeatedly arranged. The maximum inner diameter dimension L2 connecting the convex portion of the internal space S of the vibration damping member 14 and the convex portion on the opposite side through the center point of the internal space S is larger than the outer diameter dimension D of the flexible member 10, and the internal space A minimum inner diameter L1 that connects the concave portion of S and the concave portion on the opposite side through the center point of the internal space S is larger than the outer diameter D of the flexible member 10. Thus, when the vibration damping member 14 is assembled with the flexible member 10, the vibration damping member 14 is positioned between the eight contact portions 17 that are always in contact with the outer peripheral surface of the flexible member 10, and the outer periphery of the flexible member 10. There are 18 spaced portions 18 that do not contact the surface, and the surface 17 a of the contact portion 17 presses the flexible member 10 relatively loosely by deformation of the separated portion 18. That is, the maximum static frictional force generated between the damping member 14 and the flexible member 10 is a measured value of 35 Newtons to 75 Newtons, more preferably 50 Newtons to 60 Newtons.

  The damping member 14 shown in FIG. 16 has an unbalanced shape having two corners in which the outer shape is a combination of a semicircular portion and a quadrangular portion when viewed from the axial direction, and the internal space. S also has an unbalanced shape having two corners in which the semicircular portion and the quadrangular portion are combined while being similar to the outer shape of the damping member 14 as viewed from the axial direction. The maximum inner diameter dimension L2 connecting the corner of the rectangular portion of the internal space S of the damping member 14 and the semicircular portion side end through the center point of the internal space S is larger than the outer diameter dimension D of the flexible member 10, The minimum inner diameter dimension L1 that is also the dimension in the diameter direction of the semicircular portion of the internal space S is larger than the outer diameter dimension D of the flexible member 10. Thereby, when the damping member 14 is assembled with the flexible member 10, the two contact portions 17 that always contact the outer peripheral surface of the flexible member 10 (one of the contact portions 17 is the same as the edge line of the semicircular portion). ), Two spaced-apart portions 18 that are located between the contact portions 17 and do not contact the outer peripheral surface of the flexible member 10, and the surface 17 a of the contact portion 17 relative to the flexible member 10 due to deformation of the separated portion 18. It is designed to press gently. That is, the maximum static frictional force between the damping member 14 and the flexible member 10 is a measured value of 35 Newtons to 75 Newtons, more preferably 50 Newtons to 60 Newtons.

  Therefore, even with the vibration damping member 14 shown in FIGS. 11 to 16, similarly to the experimental results shown in FIGS. 9 and 10 of the vibration damping member 14 shown in FIGS. It is possible to dampen the vibration of the generation source of the compressor 2 and the like from the second hard pipe 9 to the first hard pipe 8.

  Furthermore, as a structure for mounting the damping member 14 on the outer surface of the flexible member 10, the breaking line B extending linearly along the axial direction of the damping member 14 has been shown, but is not necessarily limited thereto. As shown in FIG. 17, a breaking line B that spirally extends from one end to the other end along the axial direction of the damping member 14 may be formed. According to this, the damping member 14 deformed by the exterior of the flexible member 10 generates a force to return to the original state, and the damping member 14 presses the flexible member 10 relatively loosely by this force. It will be something that can be done. Therefore, when the breaking line B is spiral as shown in FIG. 17, the shape of the internal space S may be a perfect circle although not shown.

  Furthermore, although not shown, the damping member 14 does not have to have a shape covering the entire range in the circumferential direction with respect to the flexible member 10, and may have a substantially C shape when viewed from the axial direction. And the damping member 14 is good also as what has the cylindrical constrained layer site | part formed with the raw material harder than the said site | part on the outer peripheral side of the site | part shown by FIG. 12, for example. In this case, for example, foamed EPDM is used for the inner part of the damping member 14, and solid EPDM is used for the constrained layer part. By using the vibration damping member 14 having such a configuration, the vibration damping member 14 can more effectively consume vibration energy generated by the vibration of the flexible member 10, and the amount of vibration attenuation is also relatively large. Become.

FIG. 1 is a schematic configuration diagram showing a refrigeration cycle for a vehicle using a vibration damping member according to the present invention. Fig.2 (a) is explanatory drawing which shows the structure which mounted | wore one damping member over the perimeter of the flexible member of piping, FIG.2 (b) is sectional drawing of Fig.2 (a). Fig.3 (a) is explanatory drawing which shows the structure which mounted | wore with two damping members in a part of flexible member of piping, and FIG.3 (b) is sectional drawing of Fig.3 (a). FIG. 4A is an explanatory view showing the shape of the vibration damping member viewed from the axial direction and the minimum inner diameter dimension and the maximum inner diameter dimension of the internal space, and FIG. It is explanatory drawing which shows the shape of the state seen from the axial direction about the flexible member, and the largest outer diameter dimension. FIG. 5A is an explanatory diagram showing a configuration when the damping member is mounted on the outer surface of the flexible member, and FIG. 5B is caused by the deformation of the separated portion of the damping member. It is explanatory drawing which shows the aspect from which the surface of the contact part of a damping member becomes the force which presses a flexible member. FIG. 6 is an explanatory diagram showing that absorption is possible even if there is a dimensional error between the minimum inner diameter dimension and the maximum inner diameter dimension of the internal space of the vibration damping member. FIG. 7 is a perspective view for showing the shape of the breaking line of the damping member. FIG. 8A shows an experiment of how much vibration attenuation occurs in the first hard pipe when the frequency generated by applying vibration to the second hard pipe passes through the flexible member and the damping member. FIG. 8 (b) is an explanatory diagram showing a mode for the above, and FIG. 8B shows a case where the vibration damping member is not mounted and a case where the vibration suppression member is mounted relatively tight, obtained as an experimental result in the above mode. FIG. 6 is a characteristic diagram showing a difference in vibration attenuation between the case where the damping member is mounted relatively loosely. FIG. 9 shows an experimental result on how much maximum static frictional force should be pressed against the damping member when the flexible member with the damping member is bent at an angle of 45 degrees. FIG. FIG. 10 shows an experimental result on how much maximum static frictional force should be pressed against the damping member when the flexible member with the damping member is bent at an angle of 90 degrees. FIG. FIG. 11 is an explanatory view showing a state of the vibration damping member other than that shown in FIG. 2 as viewed from the axial direction of the vibration damping member. 12 is an explanatory view showing a state of the vibration damping member other than that shown in FIGS. 2 and 11 as seen from the axial direction of the vibration damping member. FIG. 13 is an explanatory view showing a state of the vibration damping member other than those shown in FIG. 2, FIG. 11, and FIG. 12, as viewed from the axial direction of the vibration damping member. FIG. 14 is an explanatory view showing a state of the vibration damping member other than that shown in FIG. 2 and FIGS. 11 to 13 as viewed from the axial direction of the vibration damping member. FIG. 15 is an explanatory view showing a state of the vibration damping member other than that shown in FIG. 2 and FIGS. 11 to 14 as viewed from the axial direction of the vibration damping member. FIG. 16 is an explanatory view showing a state of the vibration damping member other than that shown in FIG. 2 and FIGS. 11 to 15 as viewed from the axial direction of the vibration damping member. FIG. 17 is a perspective view showing another example of the embodiment shown in FIG. 7 as the structure of the breaking line of the damping member.

Explanation of symbols

7 Piping 8 First hard pipe (first pipe member)
9 Second hard pipe (second pipe member)
DESCRIPTION OF SYMBOLS 10 Flexible member 14 Damping member 17 Contact part 18 Separation part S Internal space of damping member B Break line of damping member L1 Minimum inside diameter size of inside space of damping member L2 Maximum inside diameter size of inside space of damping member

Claims (7)

A flexible member that is elastic and can be bent in any direction and allows fluid to pass through the inside thereof; a first pipe member connected to one end in the longitudinal direction of the flexible portion; and A pipe comprising at least a second pipe member connected to the other end in the longitudinal direction of the flexible member, and an internal space formed of an elastic body and open on both sides so as to be mounted on the outer peripheral side of the flexible member Consisting of damping members,
The vibration damping member is arranged on the flexible member so that the numerical value of the maximum static frictional force generated between the flexible member and the vibration damping member is 35 to 75 newtons, more preferably 50 to 60 newtons. A piping vibration damping structure characterized in that the flexible member is sheathed so that it can be pressed relatively loosely. A flexible member that is elastic and can be bent in any direction and allows fluid to pass through the inside thereof; a first pipe member connected to one end in the longitudinal direction of the flexible portion; and A pipe comprising at least a second pipe member connected to the other end in the longitudinal direction of the flexible member, and an internal space formed of an elastic body and open on both sides so as to be mounted on the outer peripheral side of the flexible member Consisting of damping members,
The vibration damping member is set such that the minimum inner diameter dimension of the inner space is smaller than the outer diameter dimension of the flexible member, and the maximum inner diameter dimension of the inner space is larger than the outer diameter dimension of the flexible member, When assembled with the flexible member, the flexible member is positioned between one or more contact portions that are always in contact with the outer peripheral surface of the flexible member, and between the plurality of contact portions or both ends of the one contact portion. Having a separation portion that does not always contact the outer peripheral surface,
In the internal space, when the contact portion is assembled to the flexible member, the separation portion is deformed, and the force generated by the deformation is changed to a force by which the contact portion presses the outer peripheral surface of the flexible member inward. The piping damping structure is characterized in that the damping member is configured to be able to press the flexible member relatively loosely.   The minimum inner diameter dimension and the maximum inner diameter dimension of the internal space are the numerical values of the maximum static friction force generated between the flexible member and the damping member when the damping member presses the flexible member relatively loosely. The piping damping structure according to claim 2, wherein the piping damping structure is set to be 35 Newtons to 75 Newtons.   The minimum inner diameter dimension and the maximum inner diameter dimension of the internal space are the numerical values of the maximum static frictional force generated between the flexible member and the damping member when the damping member presses the flexible member relatively loosely. The piping damping structure according to claim 2, wherein the piping damping structure is set to be from 50 Newtons to 60 Newtons. A flexible member that is elastic and can be bent in any direction and allows fluid to pass through the inside, a first pipe member connected to one end in the longitudinal direction of the flexible member, and A pipe consisting of at least a second pipe member connected to the other end in the longitudinal direction of the flexible member, and a damping member formed of an elastic body and disposed on the outer peripheral side of the flexible member are used.
About this vibration damping member, the minimum inner diameter dimension of the inner space is larger than the outer diameter dimension of the flexible member, and the maximum inner diameter dimension of the inner space is smaller than the outer diameter dimension of the flexible member, When assembled with the flexible member, it has a contact portion that is always in contact with the outer peripheral surface of the flexible member, and a separation portion that is located between the contact portions and does not contact the outer peripheral surface of the flexible member, A piping vibration damping method comprising assembling the flexible member and the vibration damping member and pressing a contact portion of the vibration damping member relatively loosely against the flexible member. A caulking member into which the flexible member can be inserted and the first or second pipe member can be inserted is further used.
6. The method according to claim 5, further comprising: passing the flexible member through the damping member; and inserting and caulking the flexible member and the first or second pipe member into the caulking member. Piping vibration control method. The damping member has a cut extending from one end in the axial direction of the damping member toward the other end, and is configured to develop so that the cut becomes an end face.
The pipe damping method according to claim 6, further comprising a step of winding the damping member around the flexible member.

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