Air conditioning system and method for manufacturing an air conditioning system

Abstract

To provide an air conditioning system that can reduce stick-slip noise in sliding parts and improve recyclability. [Solution] The air conditioning system comprises actuators (22, 50), first components (23-28, 51-54, 71, 72, 81, 90), and second components (23-28, 51-54, 71, 72, 81, 90) that slide against the first components when driven by the actuators. The sliding portion where the first and second components slide is configured such that the static friction coefficient difference (Δμ), the sliding speed (V), and the load (W) of the sliding portion are set so that the SS noise is below a predetermined volume.

Description

[Technical Field]

[0001] This disclosure relates to an air conditioning system installed in a vehicle and a method for manufacturing the same. [Background technology]

[0002] In recent years, material recycling (hereinafter simply referred to as "recycling") of resin components that make up air conditioning systems has been promoted. From this recycling perspective, the grease applied to the sliding parts of the link mechanisms that drive the various doors of air conditioning systems, or to the sliding parts of shafts and bearings, is a factor in the deterioration of the physical properties of recycled products. However, if the grease applied to the sliding parts of air conditioning systems is eliminated or reduced, problems such as stick-slip noises from the sliding parts will occur.

[0003] Patent Document 1 discloses a test method for stick-slip in elastomer materials such as resins and rubbers. This test method evaluates the likelihood of stick-slip occurring based on the quotient between the static friction coefficient and the kinetic friction coefficient, which are calculated by sliding two parts under a constant load. [Prior art documents] [Patent Documents]

[0004] [Patent Document 1] Japanese Patent Publication No. 2005-17064 [Overview of the project] [Problems that the invention aims to solve]

[0005] The test method described in Patent Document 1 uses only the value of the quotient of the static friction coefficient and the dynamic friction coefficient as the evaluation criterion for the likelihood of stick-slip. However, for the occurrence requirements of stick-slip noise in the sliding part of an air conditioner mounted on a vehicle, in addition to the static friction coefficient and the dynamic friction coefficient, it is necessary to consider the operating conditions of the air conditioner and the like. Therefore, the test method described in Patent Document 1 makes it difficult to prevent stick-slip from occurring in the sliding part of the air conditioner when the grease applied to the sliding part is abolished or reduced, or to make the volume of the stick-slip noise inaudible to the passengers.

[0006] In view of the above points, an object of the present disclosure is to provide an air conditioner capable of reducing stick-slip noise in a sliding part and improving recyclability, and a method for manufacturing the air conditioner.

Means for Solving the Problems

[0007] According to one aspect of the present disclosure, an air conditioner mounted on a vehicle includes actuators (22, 50), first components (23 to 28, 51 to 54, 71, 72, 81, 90) that constitute a part of the air conditioner, second components (23 to 28, 51 to 54, 71, 72, 81, 90) that constitute a part of the air conditioner and slide with the first components by driving the actuators, and In the sliding part where the first component and the second component slide, the difference (Δμ) between the static friction coefficient and the dynamic friction coefficient in the sliding part, the sliding speed (V) of the sliding part when the actuator is driven, and the load (W) acting on the sliding part are set so that the stick-slip noise is below a predetermined volume inaudible to the passengers.

[0008] In the following description, stick-slip noise is referred to as "SS noise." The difference between the static friction coefficient and the dynamic friction coefficient at the sliding part is referred to as the "difference in static-dynamic friction coefficients Δμ at the sliding part," the sliding speed of the sliding part when the actuator is driven is referred to as the "sliding speed of the sliding part," and the load acting on the sliding part is referred to as the "load on the sliding part." Furthermore, in this disclosure, "a predetermined volume at which the SS noise is not audible to the occupants" includes both the fact that the SS noise generated at the sliding part is not audible to the occupants, and that no SS noise is generated at the sliding part (i.e., no SS noise is produced).

[0009] According to this, the inventors have found that by adjusting the relationship between three items—the difference in static-dynamic friction coefficient Δμ of the sliding part, the sliding speed of the sliding part, and the load on the sliding part—the SS noise can be reduced to a predetermined volume even if the grease on the sliding part is eliminated or reduced. For example, if the sliding speed and load on the sliding part are fixed, the SS noise can be reduced to a predetermined volume by setting the difference in static-dynamic friction coefficient Δμ of the sliding part. Also, if the difference in static-dynamic friction coefficient Δμ and the sliding speed of the sliding part are fixed, the SS noise can be reduced to a predetermined volume by setting the load on the sliding part. Furthermore, if the difference in static-dynamic friction coefficient Δμ and the load on the sliding part are fixed, the SS noise can be reduced to a predetermined volume by setting the sliding speed of the sliding part. As a result, the air conditioning device of this disclosure can eliminate or reduce the grease that was applied to the sliding part of conventional air conditioning devices, thereby improving recyclability.

[0010] According to another aspect of this disclosure, a method for manufacturing an air conditioning system mounted on a vehicle, comprising actuators (22, 50), first components (23-28, 51-54, 71, 72, 81, 90), and second components (23-28, 51-54, 71, 72, 81, 90) that slide with the first components when driven by the actuators, is: This includes setting the difference between the static friction coefficient and the kinetic friction coefficient (Δμ) in the sliding part where the first part and the second part slide against each other, the sliding speed of the sliding part when the actuator is driven (V), and the load (W) acting on the sliding part, so that the stick-slip sound is below a predetermined volume that is inaudible to the occupants.

[0011] According to this, the invention, in another aspect of the present disclosure, can also eliminate or reduce the amount of grease applied to the sliding parts of conventional air conditioning systems, thereby improving the recyclability of air conditioning systems.

[0012] The reference numerals in parentheses attached to each component indicate an example of the correspondence between that component and the specific components described in the embodiments described later. [Brief explanation of the drawing]

[0013] [Figure 1] This is a schematic diagram of an air conditioning system according to the first embodiment. [Figure 2] This is an explanatory diagram of the first link mechanism that drives the air outlet mode door of the air conditioning unit. [Figure 3] This is a plan view of the first link plate. [Figure 4] This is an explanatory diagram of the second link mechanism that drives the exterior and interior doors of the air conditioning unit. [Figure 5] This is a front view of the drive shaft, shaft cap, and bearing section for the air mix door. [Figure 6] This graph shows the relationship between the sliding speed of the sliding part, the load, and the difference in the static friction coefficient. [Figure 7] This is a flowchart showing a part of the manufacturing method of the air conditioning system according to the first embodiment. [Figure 8] This is a schematic diagram of the air conditioning case, shaft, and bearing section of the comparative example air conditioning system. [Figure 9] This is a view from the arrow pointing in the IX direction in Figure 8. [Figure 10] This is an enlarged view of the X portion in Figure 9. [Figure 11] This figure shows the changes in the area shown in Figure 10 over time. [Figure 12] This graph shows the relationship between the sliding speed of the sliding parts, the load, and the difference in the static friction coefficient in the comparative example air conditioning system. [Figure 13] This is a schematic diagram of the air conditioning case, shaft, and bearing section of the air conditioning device according to the second embodiment. [Figure 14]This is an enlarged view of section XIV in Figure 13. [Figure 15] This is a view from the XV direction in Figure 14. [Figure 16] This graph shows the relationship between the sliding speed of the sliding part, the load, and the difference in the static friction coefficient of the sliding part in the air conditioning system according to the second embodiment. [Figure 17] This is a flowchart showing a part of the manufacturing method of the air conditioning system according to the second embodiment. [Figure 18] This graph shows the relationship between the sliding speed of the sliding part, the load, and the difference in the static friction coefficient of the air conditioning system according to the third embodiment. [Figure 19] This is a flowchart showing a part of the manufacturing method of the air conditioning system according to the third embodiment. [Modes for carrying out the invention]

[0014] The embodiments of this disclosure will be described below with reference to the drawings. In the following embodiments, parts that are the same or equivalent to each other will be denoted by the same reference numerals, and their descriptions will be omitted.

[0015] (First Embodiment) The air conditioning system according to the first embodiment is mounted on a vehicle and provides air conditioning for the vehicle interior. As shown in Figures 1, 2, and 4, the air conditioning system includes an air conditioning case 1, an outside air door 2, an inside air door 3, a blower 4, a cooling device 5, a heating device 6, an air mix door 7, outlet mode doors 8, 9, and 10, and link mechanisms 11 and 12 that drive each door.

[0016] As shown in Figure 1, the air conditioning case 1 constitutes the outer shell of the air conditioning unit. The air conditioning case 1 is molded from a resin (e.g., polypropylene) that has a certain degree of elasticity and excellent strength. An air passage 13 is formed inside the air conditioning case 1 through which air flows.

[0017] The air conditioning case 1 has an outside air inlet 14 for introducing outside air (hereinafter referred to as "outside air") into the ventilation passage 13 and an inside air inlet 15 for introducing inside air (hereinafter referred to as "inside air") into the ventilation passage 13, both located on the upstream side in the airflow direction of the ventilation passage 13. Near the outside air inlet 14, an outside air door 2 is provided to adjust the opening area of ​​the outside air inlet 14. Similarly, near the inside air inlet 15, an inside air door 3 is provided to adjust the opening area of ​​the inside air inlet 15. By driving the outside air door 2 and the inside air door 3, the ratio of outside air to inside air introduced into the ventilation passage 13 from the outside air inlet 14 or the inside air inlet 15 is adjusted. Note that the outside air door 2 and the inside air door 3 may be a single door.

[0018] A blower 4 is provided in the ventilation passage 13 inside the air conditioning case 1. The blower 4 includes a centrifugal fan 16 and an electric motor 17, etc. When the centrifugal fan 16 rotates due to the drive of the electric motor 17, outside air or inside air is introduced into the ventilation passage 13 from the outside air inlet 14 or the inside air inlet 15, and that air (i.e., outside air or inside air) is blown into the ventilation passage 13. Note that the fan in the blower 4 is not limited to a centrifugal fan 16; for example, an axial flow fan or a cross-flow fan may also be used.

[0019] The cooling device 5 is an evaporator that, together with a compressor, condenser, and expansion valve (not shown), constitutes a vapor compression type refrigeration cycle. A refrigerant in a two-layer vapor-liquid state flows inside the tube (not shown) of the evaporator. The evaporator evaporates the refrigerant through heat exchange between the refrigerant flowing inside the tube and the air flowing through the air passage 13, thereby cooling the air flowing through the air passage 13. Note that the cooling device 5 is not limited to an evaporator; for example, it may be composed of a heat exchanger through which chilled water (e.g., Long Life Coolant) flows.

[0020] The heating device 6 is installed downstream of the cooling device 5 in the direction of airflow. The heating device 6 is a heater core through which hot water flows inside a tube (not shown). The heater core heats the air flowing through the air passage 13 by heat exchange between the hot water flowing inside the tube and the air flowing through the air passage 13. Note that the heating device 6 is not limited to a heater core, but may also consist of, for example, a condenser or PCT heater of a refrigeration cycle, or they may be installed together.

[0021] An air mix door 7 is provided in the ventilation passage 13 between the cooling equipment 5 and the heating equipment 6. The air mix door 7 is, for example, a sliding door and is driven by an air mix door drive shaft 18 (hereinafter referred to as "A / M shaft 18"). The air mix door 7 adjusts the ratio of the amount of air that passes through the cooling equipment 5 and bypasses the heating equipment 6 to the amount of air that passes through the cooling equipment 5 and then passes through the heating equipment 6.

[0022] The air conditioning case 1 has multiple outlet openings on the downstream side in the airflow direction of the ventilation passage 13. The multiple outlet openings consist of a defroster outlet opening 19, a face outlet opening 20, and a foot outlet opening 21, among others. The defroster outlet opening 19 is an opening through which air flows towards the vehicle's front windshield. The face outlet opening 20 is an opening through which air flows towards the upper body of an occupant seated in the front seat of the vehicle. The foot outlet opening 21 is an opening through which air flows towards the lower body of the occupant.

[0023] The defroster outlet 19, face outlet 20, and foot outlet 21 are each provided with outlet mode doors 8, 9, and 10 for opening and closing their respective openings. The outlet mode doors 8, 9, and 10 consist of a defroster door 8, a face door 9, and a foot door 10. The defroster door 8 opens and closes the defroster outlet 19. The face door 9 opens and closes the face outlet 20. The foot door 10 opens and closes the foot outlet 21. This adjusts the airflow of the conditioned air blown out from the defroster outlet 19, face outlet 20, and foot outlet 21, respectively, and switches between various outlet modes. The above describes an example of the configuration of an air conditioning system.

[0024] Next, we will describe an example of a configuration for driving the various doors provided by an air conditioning system. As shown in Figure 2, the air outlet mode doors 8, 9, and 10 are driven by a first link mechanism 11. The first link mechanism 11 comprises a first actuator 22, a first link plate 23, and a plurality of link levers 24 to 28. The first link plate 23 and the plurality of link levers 24 to 28 are made of resin. The first link plate 23 and the plurality of link levers 24 to 28 are examples of the "first component" and "second component" provided in the air conditioning system. The first component and the second component are parts that slide against each other when driven by the actuator.

[0025] The first actuator 22 has a drive gear 29 that is rotated by a motor (not shown) and a shaft portion 30 for supporting the first link plate 23. The drive gear 29 rotates around its own axis CL1. The motor of the first actuator 22 is controlled by an air conditioning control device (not shown). The air conditioning control device is an electronic control device consisting of a processor that performs control processing and calculation processing, a microcomputer that includes memory such as ROM and RAM for storing programs and data, and peripheral circuits. Based on signals input from various sensors and switches mounted on the vehicle, the processor performs various control processing and calculation processing based on a program stored in memory, and controls the driving of the motors of each actuator.

[0026] As shown in Figures 2 and 3, the first link plate 23 is formed in a disc shape and has a central hole 31, an outer gear 32, a first groove 33 and a second groove 34, etc. The shaft portion 30 of the first actuator 22 is inserted into the central hole 31 located in the center of the first link plate 23. The outer gear 32 located on the outer circumference of the first link plate 23 meshes with the drive gear 29 of the first actuator 22. As a result, when the drive gear 29 of the first actuator 22 rotates, the first link plate 23 rotates with the center of the central hole 31 as its axis CL2. The first groove 33 is provided on one side of the first link plate 23 facing in the thickness direction, and the second groove 34 is provided on the other side facing in the thickness direction. The first groove 33 and the second groove 34 extend in a curved shape in the in-plane direction of the first link plate 23.

[0027] The multiple link levers include the first to fifth link levers 24 to 28. The first link lever 24 and the second link lever 25 are components that transmit power from the first link plate 23 to the defroster door 8. The third link lever 26 is a component that transmits power from the first link plate 23 to the face door 9. The fourth link lever 27 and the fifth link lever 28 are components that transmit power from the first link plate 23 to the foot door 10.

[0028] Specifically, the first link lever 24 has two pins 35 and 36. One pin 35 of the first link lever 24 fits into the first groove 33 of the first link plate 23 and slides inside the first groove 33. The other pin 36 of the first link lever 24 fits into the elongated groove 37 of the second link lever 25 and slides inside the groove 37. Note that the other pin 36 of the first link lever 24 is located on the far side of Figure 2, and is therefore shown with a dashed line in Figure 2. The second link lever 25 has a groove 37 into which the other pin 36 of the first link lever 24 slides, and a fixing hole 39 into which the shaft portion 38 of the defroster door 8 is inserted. The shaft portion 38 of the defroster door 8 is fixed to the fixing hole 39 of the second link lever 25.

[0029] The third link lever 26 has a pin 40 and a fixing hole 41. The pin 40 of the third link lever 26 fits into the third groove 42 of the first link plate 23 and slides inside the third groove 42. The shaft portion 43 of the face door 9 is fixed to the fixing hole 41 of the third link lever 26.

[0030] The fourth link lever 27 has a pin 44 and a groove 45. The pin 44 of the fourth link lever 27 fits into the second groove 34 of the first link plate 23 and slides inside the second groove 34. The fifth link lever 28 has a pin 46 and a fixing hole 47. The pin 46 of the fifth link lever 28 fits into the elongated groove 45 of the fourth link lever 27 and slides inside the groove 45. The shaft portion 48 of the foot door 10 is fixed to the fixing hole 47 of the fifth link lever 28.

[0031] With the above configuration, the first link mechanism 11 rotates the first link plate 23 by driving the first actuator 22, and transmits power to each of the blowing mode doors 8, 9, and 10 via the first to fifth link levers 24 to 28, making it possible to open each of the blowing mode doors 8, 9, and 10 to any desired degree.

[0032] Next, as shown in Figure 4, the exterior door 2 and the interior door 3 are driven by a second link mechanism 12. The second link mechanism 12 comprises a second actuator 50, a second link plate 51, and a plurality of link levers 52-54. The second link plate 51 and the plurality of link levers 52-54 are also made of resin. The second link plate 51 and the plurality of link levers 52-54 are also examples of the "first part" and "second part".

[0033] The second actuator 50 has a drive gear 55 that is rotated by a motor (not shown). The second link plate 51 is formed in a disc shape and has a central gear 56, a third groove 57 and a fourth groove 58, etc. The central gear 56 of the second link plate 51 meshes with the drive gear 55 of the second actuator 50. As a result, when the drive gear 55 of the second actuator 50 rotates, the second link plate 51 rotates with the center of the central gear 56 as its axis CL3. The third groove 57 and the fourth groove 58 are provided on one side of the second link plate 51 facing in the thickness direction. Although not shown, the third groove 57 and the fourth groove 58 extend in a curved shape in the in-plane direction of the first link plate 23.

[0034] The multiple link levers include the 6th to 8th link levers 52 to 54. The 6th link lever 52 is a component that transmits power from the 2nd link plate 51 to the exterior door 2. The 7th link lever 53 and the 8th link lever 54 are components that transmit power from the 2nd link plate 51 to the interior door 3.

[0035] Specifically, the sixth link lever 52 has a pin 59 and a fixing hole 60. The pin 59 of the sixth link lever 52 fits into the third groove 57 of the second link plate 51 and slides inside the third groove 57. The shaft portion 61 of the outside air door 2 is fixed to the fixing hole 60 of the sixth link lever 52.

[0036] The seventh link lever 53 has two pins 62 and 63. One pin 62 of the seventh link lever 53 fits into the fourth groove 58 of the second link plate 51 and slides inside the fourth groove 58. The other pin 63 of the seventh link lever 53 fits into the elongated groove 64 of the eighth link lever 54 and slides inside the groove 64. The eighth link lever 54 has a fixing hole 66 into which the shaft portion 65 of the interior door 3 is inserted. The shaft portion 65 of the interior door 3 is fixed to the fixing hole 66 of the eighth link lever 54.

[0037] With the above configuration, the second link mechanism 12 rotates the second link plate 51 by driving the second actuator 50, and transmits power to the outer door 2 and the inner door 3 via the sixth to eighth link levers 52 to 54, making it possible to open the outer door 2 and the inner door 3 to any desired degree.

[0038] Next, as shown in Figure 5, the A / M shaft 18 that drives the air mix door 7 has a gear 68 in the direction in which its axis CL4 extends. Hereafter, the direction in which the axis extends will be referred to as the "axis direction". The gear 68 of the A / M shaft 18 meshes with the plane gear 70 of the air mix door 7. As a result, when the A / M shaft 18 rotates around its axis CL4, the air mix door 7 is driven.

[0039] The ends of the A / M shaft 18 are fitted into holes 74 in the shaft cap 71. The A / M shaft 18 and the shaft cap 71 are made of resin. The shaft cap 71 is rotatably supported by a bearing portion 72 provided in the air conditioning case 1. The shaft cap 71 and the bearing portion 72 are also examples of the "first part" and "second part".

[0040] A gear 73 is provided on the outer circumference of the portion of the shaft cap 71 that protrudes to the outside of the air conditioning case 1. When torque is transmitted from an actuator (not shown) to the gear 73 of the shaft cap 71, the A / M shaft 18 rotates together with the shaft cap 71, and the air mix door 7 is driven. The above describes an example of a configuration for driving various doors of an air conditioning system.

[0041] Incidentally, conventionally, lubricating grease has been applied to sliding parts where multiple components slide against each other, such as the link mechanisms 11 and 12 of the various doors of air conditioning units, or the A / M shaft 18 and bearing section 72. From the perspective of material recycling of resin parts (hereinafter simply referred to as "recycling"), this grease becomes a foreign substance to the resin material and is a factor in the deterioration of the physical properties of recycled products. However, if the grease applied to the sliding parts of air conditioning units is abolished or reduced, problems such as stick-slip noise (hereinafter referred to as "SS noise") will occur from the sliding parts. SS noise refers to the sound that occurs when multiple components in a sliding part alternate between a stationary state and a sliding state.

[0042] The inventors of this disclosure have found that in an air conditioning system for a vehicle, a configuration that eliminates grease in the sliding parts and maintains a noise level below a predetermined level that is inaudible to the occupants can be designed based on the following equations 1 and 2. Note that "a predetermined noise level that is inaudible to the occupants" includes both the fact that the noise generated in the sliding parts is inaudible to the occupants, and that no noise is generated in the sliding parts (i.e., no noise is produced). In the following description, the predetermined noise level that is inaudible to the occupants will simply be referred to as "the predetermined noise level."

[0043] Δμ = A × V / W ... (Equation 1) A=f(m, c, k) (Formula 2)

[0044] However, Δμ in Equation 1 is the difference between the static friction coefficient and the kinetic friction coefficient of the sliding part at which the SS sound reaches a predetermined volume. V is the sliding speed of the sliding part when the actuator is driven. W is the load acting on the sliding part. f(m, c, k) is a function of m, c, and k. m is the mass of the two parts that make up the sliding part. c is the stiffness of the two parts that make up the sliding part, i.e., the spring constant. k is the damping coefficient of the two components that make up the sliding part.

[0045] In the following explanation, the difference between the static friction coefficient and the dynamic friction coefficient of the sliding part is referred to as the "difference in static and dynamic friction coefficients of the sliding part Δμ". The sliding speed of the sliding part when the actuator is driven is referred to as the "sliding speed V of the sliding part". The load acting on the sliding part is referred to as the "load W of the sliding part".

[0046] In equation 2 above, m, c, and k are values ​​determined by the shape and material of the two parts that constitute the sliding part. Therefore, once the two parts are determined, A becomes a constant. Accordingly, the inventors have found that the presence or absence of SS noise in the sliding part is determined by the relationship between three items: "the difference in static-dynamic friction coefficients Δμ of the sliding part", "the sliding speed V of the sliding part", and "the load W of the sliding part".

[0047] Figure 6 shows the above equation 1 as a graph. In Figure 6, the horizontal axis represents the sliding speed V of the sliding part, and the vertical axis represents the load W of the sliding part. The hatched area within the rectangle in the graph indicates the range of sliding speed V and load W of the sliding part under various operating conditions of the sliding parts of a vehicle air conditioning system. Hereinafter, this area will be referred to as the "HVAC sliding area."

[0048] Each line Δμ_ in Figure 6 X , Δμ_ CR , Δμ_ Y , Δμ_ Z Each line indicates the line at which the static-dynamic friction coefficient difference Δμ, determined by the material selection of the sliding part, results in a predetermined volume of SS sound. CR , Δμ_ X , Δμ_ Y , Δμ_ ZThe larger the slope, the smaller the difference Δμ between the static and kinetic friction coefficients of the sliding part. That is, the magnitude of the difference Δμ between the static and kinetic friction coefficients of the sliding part is Δμ_ X <Δμ_ CR <Δμ_ Y <Δμ_ Z is in the relationship of. Specifically, the solid line Δμ_ X has a smaller difference Δμ between the static and kinetic friction coefficients of the sliding part than the dashed-dotted line Δμ_ CR . The solid line Δμ_ Y has a larger difference Δμ between the static and kinetic friction coefficients of the sliding part than the dashed-dotted line Δμ_ CR . The solid line Δμ_ Z has a larger difference Δμ between the static and kinetic friction coefficients of the sliding part than the solid line Δμ_ Y .

[0049] In the graph, for each line Δμ_ X , Δμ_ CR , Δμ_ Y , Δμ_ Z , the lower-right region is the region where the SS sound is below a predetermined volume (i.e., the region where the SS sound does not sound), and the upper-left region is the region where the SS sound is greater than the predetermined volume (i.e., the region where the SS sound sounds). Therefore, each line Δμ_ X , Δμ_ CR , Δμ_ Y , Δμ_ Z can also be regarded as the boundary line between the region where the SS sound is below the predetermined volume and the region where the SS sound is greater than the predetermined volume.

[0050] The dashed-dotted line Δμ_ CR in FIG. 6 shows the limiting difference Δμ between the static and kinetic friction coefficients at the sliding speed V1 and load W1 of the sliding part, which are the most severe conditions for the SS sound to be likely to sound in the HVAC sliding region. The limiting difference Δμ between the static and kinetic friction coefficients Δμ_<00​​​​​​This allows the SS noise to be kept below a predetermined volume level across the entire range of the HVAC sliding region. On the other hand, the solid line Δμ_ Y This is the solid line Δμ_ in the HVAC sliding region. Y In the range below this, the SS sound can be reduced to a predetermined volume or less (i.e., the SS sound does not occur), but in the HVAC sliding region, the solid line Δμ_ Y In the range above this, the SS sound becomes louder than the predetermined volume (i.e., the SS sound is emitted). Solid line Δμ_ Z This means that the SS noise becomes louder than the predetermined volume over most of the HVAC sliding area (i.e., the SS noise is present over most of the HVAC sliding area).

[0051] Solid line Δμ_ X This can be achieved, for example, by forming one of the sliding parts from high-sliding polyacetal (hereinafter referred to as "high-sliding POM") and the other part from polybutylene terephthalate (hereinafter referred to as "PBT"). (Solid line Δμ_) Y This can be achieved, for example, by forming both of the two components constituting the sliding part from high-sliding POM. (Solid line Δμ_) Z For example, this product is made by forming one of the sliding parts from polyacetal (hereinafter referred to as "POM") and the other part from PBT, and corresponds to the applicant's conventional product.

[0052] For high-friction POM, for example, "NW-02" or "NW-02LV" manufactured by Polyplastics Co., Ltd. can be used. The ISO material designation for both "NW-02" and "NW-02LV" is >POM+PE<, where PE stands for polyethylene.

[0053] Based on these findings, for example, the first actuator 22, first link plate 23, second link lever 25, and fifth link lever 28 of the first link mechanism 11 described above may be formed from high-sliding POM, and the first link lever 24, third link lever 26, and fourth link lever 27 may be formed from PBT. Also, for example, the second actuator 50 and eighth link plate of the second link mechanism 12 described above may be formed from high-sliding POM, and the sixth link lever 52 and seventh link lever 53 may be formed from PBT. Furthermore, for example, the A / M shaft 18 and shaft cap 71 described above may be formed from high-sliding POM, and the bearing portion 72 may be formed from PBT.

[0054] In other words, the sliding speed V and load W (i.e., HVAC sliding region) of the sliding parts of the first link mechanism 11 and the second link mechanism 12 may be fixed in the current product. Also, it may be difficult to make significant shape changes or system changes to the first link mechanism 11 and the second link mechanism 12 from the current product. For this reason, the material of the components constituting the sliding part may be such that the limit static-dynamic friction coefficient difference Δμ_ cr By selecting a material that results in a smaller static-dynamic friction coefficient difference Δμ, it is possible to reduce SS noise to a predetermined level or lower in all sliding parts without changing the shape or system of the current product, and without the need for grease.

[0055] Furthermore, as an example of material selection for the components constituting the sliding part, forming one component with high-sliding POM and the other component with PBT is provided. That is, the material of the components constituting the sliding part is such that the difference in static-dynamic friction coefficient Δμ of the sliding part is such that the limit static-dynamic friction coefficient difference Δμ_ cr If it is smaller than that, any combination of materials can be selected.

[0056] Next, regarding the air conditioning system of the first embodiment described above, an example of its manufacturing method will be explained with reference to the flowchart in Figure 7. In the following explanation and figures, each step will simply be denoted as "S".

[0057] In Figure 7, at S1, the HVAC sliding area is measured or calculated. Specifically, for each sliding part in the air conditioning unit that is grease-free, the sliding speed V and the load W of the sliding part are measured or calculated. Next, in S2, at the sliding speed V1 and load W1 of the sliding part, which are the most severe conditions for SS noise within the HVAC sliding region, the limit static-dynamic friction coefficient difference Δμ_ is calculated based on equations 1 and 2 above. cr Calculate.

[0058] Next, in S3, the critical static-dynamic friction coefficient difference Δμ_ cr Select a combination of materials that results in a smaller difference in static-dynamic friction coefficients Δμ. Furthermore, selecting materials similar to those currently used in the product will ensure reliability and reduce costs. Then, in S4, the first and second parts that constitute the sliding part are formed using the material selected in S3. In S5, the first and second parts are assembled with the air conditioning case 1.

[0059] The air conditioning system of the first embodiment described above has the following configuration and effects. (1) The air conditioning system of the first embodiment includes a first component and a second component that slide when driven by actuators 22 and 50. The sliding portion in which the first component and the second component slide is set such that the static friction coefficient difference Δμ of the sliding portion, the sliding speed V of the sliding portion, and the load W of the sliding portion are set so that the SS sound is below a predetermined volume. According to this, the inventors have found that by adjusting the relationship between three items—the difference in static-dynamic friction coefficient Δμ of the sliding part, the sliding speed V of the sliding part, and the load W of the sliding part—the SS noise can be reduced to a predetermined volume even if the grease on the sliding part is eliminated or reduced. For example, if the sliding speed V and the load W of the sliding part are fixed, the SS noise can be reduced to a predetermined volume by setting the difference in static-dynamic friction coefficient Δμ of the sliding part. As a result, the air conditioning device of the first embodiment can eliminate or reduce the grease that was applied to the sliding part of conventional air conditioning devices, thereby improving recyclability.

[0060] (2) In the first embodiment, the first and second parts have a limit static-dynamic friction coefficient difference Δμ_ under the conditions of the sliding speed V of the sliding part and the load W of the sliding part. cr It is formed from a combination of materials that results in a static-dynamic friction coefficient difference Δμ smaller than [a certain value]. According to this, when the sliding speed V and load W of the sliding part are fixed, the difference in the limiting static-dynamic friction coefficient Δμ_ is determined under those conditions. cr By selecting materials for the first and second components that result in a smaller static-dynamic friction coefficient difference Δμ, the SS noise can be reduced to a predetermined volume or lower.

[0061] (3) In the first embodiment, one of the first and second parts is a part having grooves 31, 33, 34, 37, 42, 45, 57, 58, and 64, and the other of the first and second parts is a part having pins 30, 35, 36, 40, 44, 46, 59, 62, and 63 that slide inside the grooves, and the grooves and pins constitute a sliding part. According to this, when the sliding part is composed of grooves and pins, it is generally difficult to reduce the load W of the sliding part by changing the shape of the sliding part. Therefore, by setting the difference Δμ between the static and dynamic friction coefficients of the sliding part, the SS sound can be reduced to a predetermined volume or lower.

[0062] (4) In the first embodiment, one of the first and second parts is made of high-slidability POM, and the other of the first and second parts is made of PBT. According to this, in the HVAC sliding region, the limit static-dynamic friction coefficient difference Δμ_ cr Examples of material combinations for the first and second parts that result in a smaller static-dynamic friction coefficient difference Δμ include high-slidability POM and PBT.

[0063] Furthermore, the manufacturing method of the air conditioning system according to the first embodiment has the following configuration and effects. (5) The method for manufacturing the air conditioning device of the first embodiment includes setting the static friction coefficient difference Δμ of the sliding parts in which the first part and the second part slide, the sliding speed V of the sliding parts, and the load W of the sliding parts so that the SS sound is below a predetermined volume. According to this, this manufacturing method also makes it possible to eliminate or reduce the amount of grease applied to the sliding parts of conventional air conditioning units, thereby improving the recyclability of the air conditioning units.

[0064] (6) The manufacturing method of the air conditioning device of the first embodiment relates to the first and second components, and under the conditions of the sliding speed V of the sliding part and the load W of the sliding part, the limit static-dynamic friction coefficient difference Δμ_ cr This includes selecting a combination of materials that results in a static-dynamic friction coefficient difference Δμ smaller than [a certain value]. According to this, when the sliding speed V and load W of the sliding part are fixed, the difference in the limiting static-dynamic friction coefficient Δμ_ is determined under those conditions. cr By selecting materials for the first and second components that result in a smaller static-dynamic friction coefficient difference Δμ, the SS noise can be reduced to a predetermined volume or lower.

[0065] (Second Embodiment) A second embodiment will now be described. The second embodiment modifies the first embodiment by eliminating grease in the sliding parts of the air conditioning unit to reduce SS noise. In the first embodiment described above, the difference in static-dynamic friction coefficient Δμ of the sliding parts was reduced by selecting the material of the parts constituting the sliding parts, thereby eliminating or reducing the grease that was conventionally applied to the sliding parts and reducing the SS noise to a predetermined volume or lower. In contrast, the second embodiment achieves the same objective by reducing the load W of the sliding parts by changing the shape of the parts constituting the sliding parts.

[0066] First, before describing the air conditioning system of the second embodiment, we will describe the comparative example air conditioning system and its problems.

[0067] As shown in Figure 8, in the comparative example, a bearing portion 80 provided in the air conditioning case 1 of the air conditioning unit and a shaft 81 supported by the bearing portion 80 will be described. The shaft 81 rotates around its axis CL5. The bearing portion 80 rotatably supports the shaft 81. The air conditioning case 1 has a left wall 82, a right wall 83, and a central wall 84. In this case, the centers of the bearing portion 80 provided on the left wall 82, the center of the bearing portion 80 provided on the right wall 83, and the center of the bearing portion 80 provided on the central wall 84 may be slightly misaligned due to manufacturing tolerances, etc. The displacement amount δ of the shaft 81 in this case is, for example, 0.2 mm or less.

[0068] As shown in Figures 9 and 10, the bearing portion 80 has three triangular ribs 85 that protrude radially inward from the inner wall of the bearing hole 87 through which the shaft 81 passes. When assembling the shaft 81, the bearing portion 80 is configured such that the radially inward ends of the triangular ribs 85 are crushed by the shaft 81, and the shaft 81 is held in place by the reaction force. In the comparative example, the radially inward-facing surface 86 of the triangular ribs 85 of the bearing portion 80 and the outer wall of the shaft 81 constitute a sliding surface. The bearing portion 80 and the shaft 81 are made of resin.

[0069] Thus, in the comparative example air conditioning device, the shaft 81 and the bearing section 80 have a shape similar to a fixed-end beam. Therefore, in the comparative example air conditioning device, the assembly load between the shaft 81 and the bearing section 80 due to the misalignment of the coaxiality of the multiple bearing sections 80 provided in the air conditioning case 1 (hereinafter simply referred to as "assembly load") is derived from the following equation 3, which represents a fixed-end beam and concentrated load.

[0070] P = 192EIδ / L 3 ...(Formula 3) However, P is the assembly load, E is the modulus of elasticity, I is the second moment of area, δ is the displacement of the shaft 81, and L is the distance between the bearing portion 80 of the left wall 82 and the bearing portion 80 of the right wall 83.

[0071] The load acting on the shaft 81 and the bearing portion 80 (i.e., the load W on the sliding portion) is expressed by the following equation 4.

[0072] W=P+N (Formula 4) However, W is the load on the sliding part, P is the assembly load, and N is the holding force of the bearing part 80 in holding the shaft 81 (hereinafter simply referred to as "holding force"). In the case of the bearing section 80 in the comparative example, the holding force can be calculated from the relationship between the compression amount of the triangular rib 85 and the generated stress.

[0073] Figure 12 shows the relationship between the sliding speed V of the sliding part, the load W, and the difference in static friction coefficient Δμ in the comparative example air conditioning system.

[0074] The solid line Δμ_ shown in the graph in Figure 12 PP This line shows the point at which the static-dynamic friction coefficient difference Δμ, determined by the materials constituting the sliding part of the comparative example, results in a predetermined volume of SS sound. In the graph, the solid line Δμ_ PP The area in the lower right is the region where the SS sound is below a predetermined volume (i.e., the region where the SS sound is not emitted), and the solid line Δμ_ PP The upper left region is the region where the SS sound becomes louder than a predetermined volume (i.e., the region where the SS sound is produced). Therefore, the solid line Δμ_ PP This can also be seen as the boundary line between the region where the SS sound is below a predetermined volume and the region where the SS sound is above that predetermined volume.

[0075] In the comparative example, since the shaft 81 and bearing section 80 have a shape similar to a fixed beam at both ends, if the grease on the sliding part is eliminated, the load W2 and sliding speed V2 on the sliding part may enter a region where the SS sound becomes louder than a predetermined volume (i.e., a region where the SS sound is emitted), as shown at point C in the graph of Figure 12. Therefore, the air conditioning unit of the comparative example has the problem of emitting an SS sound when the shaft 81 rotates.

[0076] Furthermore, as shown in Figure 11, in the comparative example, if the triangular rib 85 is crushed due to the load acting on the bearing portion 80 when the shaft 81 is assembled, or due to vibrations when the air conditioning unit is used, a gap G may be created between the triangular rib 85 and the shaft 81, and the holding force may decrease. In that case, since the sliding part does not have the vibration damping and cushioning effect of grease due to the elimination of grease, there is also the problem that rattling noise will be generated from the sliding part due to the vibration of the shaft 81.

[0077] In contrast to the comparative example air conditioning system described above, the air conditioning system of the second embodiment reduces the load W of the sliding part by changing the shape of the bearing part that constitutes the sliding part, thereby eliminating or reducing the amount of grease and reducing the SS noise to a predetermined volume or lower.

[0078] As shown in Figure 13, in the second embodiment, a bearing portion 90 provided in the air conditioning case 1 of the air conditioning unit and a shaft 81 supported by the bearing portion 90 will also be described. The shaft 81 rotates around its axis CL6, and the bearing portion 90 rotatably supports the shaft 81. Due to manufacturing tolerances, the centers of the bearing portions 90 provided on the left wall 82, the right wall 83, and the central wall 84 of the air conditioning case 1 may be slightly misaligned. The displacement amount δ of the shaft 81 at this time is, for example, 0.2 mm or less.

[0079] As shown in Figures 14 and 15, the bearing portion 90 has a base portion 92 that forms a bearing hole 91 through which the shaft 81 passes, and a plurality of claw portions 94 that extend from the base portion 92 in the axial direction of the shaft 81. Specifically, the bearing portion 90 has four claw portions 94. Each of the plurality of claw portions 94 extends from the base portion 92 in the axial direction, and the surface 95 of the claw portion 94 that faces the axis CL6 of the shaft 81 (hereinafter referred to as the "sliding surface 95 of the claw portion 94") is formed to be located radially inward from the inner circumferential surface of the bearing hole 91. The sliding surfaces 95 of the plurality of claw portions 94 are in contact with the outer wall of the shaft 81. The plurality of claw portions 94 are elastically deformable in a direction intersecting the axis CL6 of the shaft 81 (in other words, the radial direction of the bearing hole 91). This bearing portion 90 is configured to hold the shaft 81 by the elastic force of the plurality of claw portions 94. In the second embodiment, the sliding surfaces 95 of the multiple claw portions 94 of the bearing portion 90 and the outer wall of the shaft 81 constitute the sliding portion. That is, the bearing portion 90 and the shaft 81 are examples of the "first component" and "second component" of the air conditioning system. The bearing portion 90 and the shaft 81 are made of resin.

[0080] Thus, in the air conditioning device of the second embodiment, the shaft 81 and the bearing portion 90 have a shape that is close to simple support. Therefore, in the air conditioning device of the second embodiment, the assembly load due to the misalignment of the coaxiality of the multiple bearing portions 90 provided in the air conditioning case 1 is derived from the following equation 5, which represents a simply supported beam and concentrated load. P = 48EIδ / L 3 ...(Formula 5)

[0081] As explained in the comparative example, the load acting on the shaft 81 and the bearing portion 90 (i.e., the load W on the sliding portion) is expressed by the following equation 4. W=P+N (Formula 4) In the case of the shape of the bearing portion 90 of the second embodiment, the holding force of the bearing portion 90 in holding the shaft 81 can be calculated from the relationship between the amount of deflection of the claw portion 94 and the elastic force.

[0082] In the second embodiment, by making the shape of the bearing portion 90 into four claw portions 94, it is possible to reduce the assembly load compared to the comparative example, and as a result, the load W of the sliding portion can be reduced.

[0083] In the air conditioning system of the second embodiment, Figure 16 shows the relationship between the sliding speed V of the sliding part, the load W, and the difference in static friction coefficient Δμ.

[0084] The solid line Δμ_ shown in the graph in Figure 16 PP This line indicates the point at which the static-dynamic friction coefficient difference Δμ, determined by the material constituting the sliding part of the second embodiment, results in a predetermined volume of SS sound. The material constituting the sliding part of the second embodiment is the same as the material constituting the sliding part of the comparative example.

[0085] In the second embodiment, since the shaft 81 and the bearing portion 90 have a shape similar to a simple beam, even if the grease on the sliding portion is eliminated, the load W3 and sliding speed V2 of the sliding portion fall into a range where the SS sound is below a predetermined volume (i.e., a range where no SS sound is produced), as shown at point D in the graph of Figure 16. Therefore, the air conditioning system of the second embodiment can reduce the SS sound to below a predetermined volume when the shaft 81 rotates.

[0086] Furthermore, in the second embodiment, the holding force of the bearing portion 90 in holding the shaft 81 can be adjusted by setting the number of claw portions 94 of the bearing portion 90, the length of contact between the claw portions 94 and the shaft 81, and the rigidity of the claw portions 94. The upper limit of the holding force is set to the limit load at which the actuator driving the shaft 81 does not lock and the SS sound is below a predetermined volume. On the other hand, the lower limit of the holding force is set to the limit load at which the rattling sound of the shaft 81 is below a volume that is inaudible to the occupants. Note that "a volume at which the rattling sound of the shaft 81 is inaudible to the occupants" includes both the fact that the rattling sound generated by the shaft 81 is inaudible to the occupants and that no rattling sound is generated.

[0087] Here, we will explain the holding force required of the bearing section 90 (i.e., the lower limit of the holding force) in order to reduce the rattling noise of the shaft 81 to a volume that is inaudible to the occupants.

[0088] In order to make the rattling noise of the shaft 81 inaudible to the passengers, it is only necessary that the frictional force required for slip suppression be large with respect to the excitation force due to vibration, that is, the following formula 6 may be satisfied. F1 < F2 ···(Formula 6) However, F1 is the excitation force mainly due to the vibration from the vehicle side. F2 is the frictional force required for slip suppression.

[0089] The excitation force due to vibration is expressed by the following formula 7. F1 = m × a ···(Formula 7) However, m is the weight of the shaft 81 and the door connected to the shaft 81. a is the vibration acceleration.

[0090] The frictional force required for slip suppression is expressed by the following formula 8. F2 = μ(m × g + N) ···(Formula 8) However, μ is the coefficient of static friction. g is the acceleration due to gravity. N is the holding force required for the bearing portion 90.

[0091] Substituting Formula 7 and Formula 8 into Formula 6, the holding force required for the bearing portion 90 is expressed by the following formula 9. N > m × (a / μ - g) ···(Formula 9)

[0092] Based on the above formula 9, by setting the length, rigidity, etc. of the claw portion 94 of the bearing portion 90 so that the required holding force of the bearing portion 90 can be obtained, the rattling noise of the shaft 81 can be made inaudible to the passengers.

[0093] Next, regarding the air conditioner of the second embodiment described above, an example of its manufacturing method will be described with reference to the flowchart of FIG. 17.

[0094] In S11 of FIG. 17, the difference Δμ in the coefficient of static and kinetic friction of the sliding portion that is grease-free in the air conditioner is measured. Next, in S12, the sliding speed V of the sliding portion is measured or calculated. Next, in S13, the range of the load W of the sliding part is set. The range of the load W of the sliding part is set to a load smaller than the load at which the SS sound reaches a predetermined value, calculated based on Equation 1 above, under the conditions of the static-dynamic friction coefficient difference Δμ measured in S11 and the sliding speed V of the sliding part measured or calculated in S12.

[0095] Next, in S14, the shape of the sliding part is designed. When the first and second parts constituting the sliding part are a bearing part 90 and a shaft 81, it is exemplified that the shape of the bearing part 90 is a plurality of claw parts 94. In this case, the upper limit of the holding force of the bearing part 90 that holds the shaft 81 is the limit load at which the actuator driving the shaft 81 does not lock and the SS sound is below a predetermined volume. On the other hand, the lower limit of the holding force is the limit load at which the rattling sound of the shaft 81 is below a volume that is not audible to the occupants. Then, in S15, the first and second parts that constitute the sliding part are formed into the shape designed in S14. In S16, the first and second parts are assembled with the air conditioning case 1.

[0096] The air conditioning system of the second embodiment described above has the following configuration and effects. (1) In the second embodiment, the load W of the sliding part is set to be smaller than the load at which the SS sound becomes a predetermined volume under the conditions of the static friction coefficient difference Δμ of the sliding part and the sliding speed V of the sliding part. According to this, if the difference in static-dynamic friction coefficients Δμ and the sliding speed V of the sliding parts are fixed, the SS noise can be reduced to a predetermined volume or lower by reducing the load W acting on the sliding parts under those conditions. Changing the shape of the sliding parts is an effective way to reduce the load W acting on the sliding parts. Therefore, by changing the shape of the sliding parts without changing the material of the sliding parts, the grease that was applied to the sliding parts of conventional air conditioning devices can be eliminated or reduced, improving recyclability.

[0097] (2) In the second embodiment, the first and second components are set such that, under the conditions of the difference in static friction coefficient Δμ of the sliding parts and the sliding speed V of the sliding parts, the upper limit of the load W of the sliding parts is set to be less than the load at which the actuator locks and less than the load at which the SS sound reaches a predetermined volume. Furthermore, the lower limit of the load W of the sliding parts is set to be greater than the load at which the rattling sound between the first and second components reaches a volume that is not audible to the occupants. This prevents the actuator from locking up and allows the SS noise to be kept below a predetermined volume. Furthermore, it allows the rattling noise of the sliding parts to be kept below a volume that is inaudible to the occupants.

[0098] (3) In the second embodiment, one of the first and second components is a bearing portion 90, and the other of the first and second components is a shaft 81, and the bearing portion 90 and the shaft 81 constitute a sliding portion. The load W acting on the sliding portion is adjusted by the shape of the bearing portion 90. According to this, when the sliding part consists of a bearing part 90 and a shaft 81, the load W of the sliding part can be reduced by changing the shape of the sliding part, and the SS sound can be reduced to a predetermined volume or lower without changing the material of the sliding part.

[0099] (4) In the second embodiment, the bearing portion 90 has a plurality of claw portions 94 that contact the outer circumferential surface of the shaft 81, and the shaft 81 is held by the elastic force of the plurality of claw portions 94. According to this, when the sliding part consists of a bearing part 90 and a shaft 81, the load W of the sliding part can be reduced by making the bearing part 90 have a shape that has multiple claw parts 94, and the SS sound can be made to a predetermined volume or lower.

[0100] (5) In the second embodiment, the holding force of the bearing portion 90 in holding the shaft 81 is adjusted by setting the number of claw portions 94 of the bearing portion 90, the length of contact between the claw portions 94 and the shaft 81, and the rigidity of the claw portions 94. According to this, the holding force of the bearing section 90 in holding the shaft 81 can be adjusted, the SS noise can be reduced to a predetermined volume or lower, and the rattling noise can be reduced to a volume that is inaudible to the occupants.

[0101] (6) In the second embodiment, the number of claws 94 of the bearing portion 90 is four. According to this, a four-claw portion 94 is given as an example of a bearing portion 90 that can reduce the SS sound to a predetermined volume or lower.

[0102] Furthermore, the manufacturing method of the air conditioning system according to the second embodiment has the following configuration and effects. (7) The method for manufacturing the air conditioning device of the second embodiment includes setting the load W acting on the sliding part to be smaller than the load W on the sliding part at which the SS sound becomes a predetermined volume under the conditions of the static friction coefficient difference Δμ of the sliding part and the sliding speed V of the sliding part. According to this, if the difference in static-dynamic friction coefficients Δμ of the sliding parts and the sliding speed V of the sliding parts are fixed, the SS noise can be reduced to a predetermined volume or lower by lowering the load W acting on the sliding parts under those conditions.

[0103] (8) The method for manufacturing the air conditioning system of the second embodiment includes setting the upper limit of the load W of the sliding part to be smaller than the load at which the actuator locks, and also smaller than the load at which the SS sound reaches a predetermined volume. Furthermore, it includes setting the lower limit of the load W of the sliding part to be larger than the load at which the rattling sound between the first and second parts reaches a volume that is not audible to the occupants. This prevents the actuator from locking up and allows the SS noise to be kept below a predetermined volume. Furthermore, it allows the rattling noise of the sliding parts to be kept below a volume that is inaudible to the occupants.

[0104] (Third embodiment) A third embodiment will now be described. Compared to the first and second embodiments, the third embodiment increases the sliding speed V of the sliding part, thereby eliminating or reducing the amount of grease that was conventionally applied to the sliding part, and also reduces the SS noise to a predetermined volume or lower.

[0105] In the air conditioning system of the third embodiment, Figure 18 shows the relationship between the sliding speed V of the sliding part, the load W, and the difference in static friction coefficient Δμ. The solid line Δμ_ shown in the graph in Figure 18 PPThis line indicates the point at which the SS sound reaches a predetermined volume at a static-dynamic friction coefficient difference Δμ determined by the material constituting the sliding part of the third embodiment. Point C in Figure 18 indicates the position of the load W2 and sliding speed V2 of the sliding part of the air conditioning device described in the comparative example above. Point E indicates the position of the load W2 and sliding speed V3 of the sliding part of the air conditioning device of the third embodiment.

[0106] In the third embodiment, when the first and second components constituting the sliding part are composed of a shaft and a bearing, the sliding speed V of the sliding part can be increased by increasing the drive speed of the actuator that drives the shaft. To increase the drive speed of the actuator, the rotational speed of the motor of the actuator can be increased or the gear ratio can be changed. On the other hand, when the first and second components constituting the sliding part are composed of a link plate and a plurality of link levers, the sliding speed V of the sliding part can also be increased by increasing the drive speed of the actuator that drives them or by changing the lever ratio.

[0107] As a result, even if the sliding parts of the first and second components of the comparative air conditioning device are at the position shown at point C in Figure 18, they can be moved to the position shown at point E in Figure 18 by increasing the sliding speed V without changing their material or shape. That is, the sliding speed V and load W of the sliding part are equal to the solid line Δμ_ PP In contrast, the SS sound enters a region below a predetermined volume (i.e., a region where no SS sound is emitted). Therefore, the air conditioning system of the third embodiment can also reduce the SS sound to below a predetermined volume.

[0108] Next, regarding the air conditioning system of the third embodiment described above, an example of its manufacturing method will be explained with reference to the flowchart in Figure 19.

[0109] In S21 of Figure 19, the difference in static-dynamic friction coefficients Δμ between the sliding parts of the air conditioning unit that are grease-free is measured. Next, in S22, the load W of the sliding part is measured or calculated. Next, in S23, the sliding speed V of the sliding part is set. The sliding speed V of the sliding part is set to a range higher than the sliding speed at which the SS sound reaches a predetermined value, calculated based on Equation 1 above, under the conditions of the static friction coefficient difference Δμ measured in S21 and the load W of the sliding part measured or calculated in S22.

[0110] Next, in S24, the actuator speed is set so that the sliding part reaches the sliding speed V set in S23. Note that if the first and second components consist of a link plate and multiple link levers, the lever ratio may be changed to ensure that the sliding part reaches the sliding speed V set in S23. Then, in S25, the first and second parts that constitute the sliding part are formed. In S26, the first and second parts are assembled into the air conditioning unit.

[0111] The air conditioning system of the third embodiment described above has the following configuration and provides the following effects. (1) In the third embodiment, the sliding speed V of the sliding parts of the first and second parts is set to be faster than the sliding speed at which the SS sound reaches a predetermined volume under the conditions of the difference in static friction coefficient Δμ of the sliding parts and the load W of the sliding parts. According to this, if the difference in static-dynamic friction coefficients Δμ of the sliding parts and the load W of the sliding parts are fixed, the SS noise can be reduced to a predetermined volume or lower by increasing the sliding speed V of the sliding parts under those conditions. Therefore, without changing the material and shape of the sliding parts, the grease applied to the sliding parts of conventional air conditioning devices can be eliminated or reduced, improving recyclability.

[0112] Furthermore, the manufacturing method of the air conditioning system according to the third embodiment has the following configuration and effects. (2) The manufacturing method of the air conditioning device according to the third embodiment includes setting the sliding speed V of the sliding parts to a speed higher than the sliding speed V at which the SS sound reaches a predetermined volume under the conditions of the static friction coefficient difference Δμ of the sliding parts and the load W of the sliding parts. According to this, if the difference in static-dynamic friction coefficients Δμ of the sliding parts and the load W of the sliding parts are fixed, the SS noise can be reduced to a predetermined volume or lower by increasing the sliding speed V of the sliding parts under those conditions.

[0113] (Other embodiments) In the first embodiment described above, the difference in static-dynamic friction coefficients Δμ was reduced by selecting the materials of the first and second components constituting the sliding part, but the invention is not limited to this. For example, the difference in static-dynamic friction coefficients Δμ of the sliding part may be reduced by applying a small amount of grease to the sliding part, such that it does not pose a problem for recycling.

[0114] This disclosure is not limited to the embodiments described above, and modifications may be made as appropriate within the scope of the claims. Furthermore, the embodiments and parts thereof are not unrelated to each other and can be combined as appropriate, except in cases where the combination is clearly impossible. In addition, it goes without saying that the elements constituting the embodiments are not necessarily essential, except in cases where they are explicitly stated to be particularly essential or where they are clearly considered essential in principle. Furthermore, in the embodiments, when numerical values ​​such as the number, numerical values, quantities, or ranges of the components of the embodiments are mentioned, the embodiments are not limited to those specific numbers, except in cases where they are explicitly stated to be particularly essential or where they are clearly limited to a specific number in principle. Furthermore, when the shapes, positional relationships, etc., of the components, etc., are mentioned in the embodiments, the embodiments are not limited to those shapes, positional relationships, etc., except in cases where they are explicitly stated to be particularly essential or where they are clearly limited to a specific shape, positional relationship, etc., in principle.

[0115] The control unit and its method described herein may be implemented by a dedicated computer provided by configuring a processor and memory programmed to perform one or more functions embodied by a computer program. Alternatively, the control unit and its method described herein may be implemented by a dedicated computer provided by configuring a processor by one or more dedicated hardware logic circuits. Alternatively, the control unit and its method described herein may be implemented by one or more dedicated computers configured by a combination of a processor and memory programmed to perform one or more functions and a processor configured by one or more hardware logic circuits. Furthermore, the computer program may be stored as instructions executed by the computer on a computer-readable non-transitional tangible recording medium. The memory described above is a non-transitional tangible storage medium. When the computer program is executed, the control method corresponding to the computer program is executed.

[0116] (Perspective of this disclosure) The above disclosure can be understood from the following perspectives, for example. [First point of view] In an air conditioning system installed in a vehicle, Actuators (22, 50) and The first components (23-28, 51-54, 71, 72, 81, 90) that constitute part of the air conditioning system, The air conditioning system comprises a second part (23-28, 51-54, 71, 72, 81, 90) which forms part of the air conditioning system and slides with the first part when driven by the actuator, An air conditioning system in which the sliding part between the first part and the second part slides is configured such that the difference between the static friction coefficient and the kinetic friction coefficient in the sliding part (Δμ), the sliding speed of the sliding part when the actuator is driven (V), and the load acting on the sliding part (W) are set so that the stick-slip sound is below a predetermined volume that is not audible to the occupants. [Second perspective] The air conditioning device according to the first aspect, wherein the first and second parts are formed of a combination of materials such that, under the conditions of the sliding speed of the sliding part when the actuator is driven, and the conditions of the load acting on the sliding part, the difference between the static friction coefficient and the dynamic friction coefficient is smaller than the difference between the static friction coefficient and the dynamic friction coefficient that results in a predetermined volume of stick-slip noise. [Third perspective] An air conditioning device according to the first or second aspect, wherein one of the first and second parts is a part having grooves (31, 33, 34, 37, 42, 45, 57, 58, 64), and the other of the first and second parts is a part having pins (30, 35, 36, 40, 44, 46, 59, 62, 63) that slide inside the grooves, and the sliding part is formed by the grooves and the pins. [Fourth perspective] One of the first and second parts is formed of a highly sliding polyacetal, An air conditioning device according to any one of the first to third aspects, wherein the other of the first and second parts is formed of polybutylene terephthalate. [Fifth perspective] The air conditioning device according to the first aspect, wherein the load acting on the sliding part is set to be smaller than the load at which the stick-slip sound produces a predetermined volume, under the conditions of the difference between the static friction coefficient and the dynamic friction coefficient of the sliding part, and the sliding speed of the sliding part when the actuator is driven. [Sixth perspective] The air conditioning device according to the first aspect, wherein, under the conditions of the difference between the static friction coefficient and the kinetic friction coefficient of the sliding part, and the sliding speed of the sliding part when the actuator is driven, the upper limit of the load acting on the sliding part is set to be less than the load at which the actuator locks and less than the load at which the stick-slip sound becomes a predetermined volume, and further, the lower limit of the load acting on the sliding part is set to be greater than the load at which the rattling sound between the first part and the second part becomes audible to the occupant. [Seventh perspective] An air conditioning device according to the fifth or sixth aspect, wherein one of the first and second parts is a bearing portion (72, 90), and the other of the first and second parts is a shaft (18, 71, 81) that slides inside the bearing portion, the bearing portion and the shaft constitute the sliding portion, and the load acting on the sliding portion is adjusted by the shape of the bearing portion. [Perspective 8] The air conditioning device according to the seventh aspect, wherein the bearing portion (90) has a plurality of claw portions (94) that contact the outer circumferential surface of the shaft, and the shaft is held by the elastic force of the plurality of claw portions which are elastically deformable in a direction intersecting the axis (CL6) of the shaft. [Perspective 9] The air conditioning device according to the eighth aspect, wherein the holding force of the bearing portion in holding the shaft is adjusted by setting the number of claws of the bearing portion, the length of contact between the claws and the shaft, and the rigidity of the claws. [Perspective 10] The air conditioning device according to the eighth or ninth aspect, wherein the number of claws is four. [Perspective 11] The air conditioning device according to the first aspect, wherein the sliding speed of the sliding part when the actuator is driven is set to be faster than the sliding speed at which the stick-slip sound becomes a predetermined volume, under the conditions of the difference between the static friction coefficient and the kinetic friction coefficient of the sliding part and the load acting on the sliding part. [Perspective 12] The sliding part is greaseless, as described in any one of the first, second, fifth, sixth, and eleventh air conditioning devices. [Perspective 13] A method for manufacturing an air conditioning system mounted on a vehicle, comprising actuators (22, 50), first components (23-28, 51-54, 71, 72, 81, 90), and second components (23-28, 51-54, 71, 72, 81, 90) that slide with the first components when driven by the actuators, A method for manufacturing an air conditioning system, comprising setting the difference between the static friction coefficient and the kinetic friction coefficient (Δμ) in the sliding part where the first part and the second part slide against each other, the sliding speed (V) of the sliding part when the actuator is driven, and the load (W) acting on the sliding part, so that the stick-slip sound is at or below a predetermined volume that is inaudible to the occupants. [Perspective 14] A method for manufacturing an air conditioning device according to the thirteenth aspect, relating to the first and second components, the method for manufacturing an air conditioning device according to the thirteenth aspect, which includes selecting a combination of materials such that the difference between the static friction coefficient and the dynamic friction coefficient is smaller than the difference between the static friction coefficient and the dynamic friction coefficient that results in the stick-slip sound of a predetermined volume, under the conditions of the sliding speed of the sliding part when the actuator is driven and the conditions of the load acting on the sliding part. [Perspective 15] A method for manufacturing an air conditioning device according to the thirteenth aspect, wherein, with respect to the first and second components, the load acting on the sliding part is set to be smaller than the load on the sliding part at which the stick-slip sound produces a predetermined volume, under the conditions of the difference between the static friction coefficient and the dynamic friction coefficient of the sliding part, and the sliding speed of the sliding part when the actuator is driven. [Perspective 16] A method for manufacturing an air conditioning system according to the 13th aspect, wherein, with respect to the first and second parts, under the conditions of the difference between the static friction coefficient and the dynamic friction coefficient of the sliding part and the sliding speed of the sliding part when the actuator is driven, the load acting on the sliding part is set as an upper limit to be less than the load at which the actuator locks and less than the load at which the stick-slip sound becomes the predetermined volume, and further, the load acting on the sliding part is set as a lower limit to be greater than the load at which the rattling sound between the first and second parts becomes the volume at which the occupant cannot hear it. [Perspective 17] A method for manufacturing an air conditioning device according to the thirteenth aspect, wherein, with respect to the first and second components, the sliding speed of the sliding part during the operation of the actuator is set to be faster than the sliding speed at which the stick-slip sound produces a predetermined volume, under the conditions of the difference between the static friction coefficient and the dynamic friction coefficient of the sliding part and the load acting on the sliding part. [Perspective 18] A method for manufacturing an air conditioning device according to any one of the 13th to 17th claims, wherein the sliding part is made grease-free. [Explanation of Symbols]

[0117] 22: First actuator, 23: First link plate, 24: First link lever, 25: Second link lever, 26: Third link lever, 27: Fourth link lever, 28: Fifth link lever, 50: Second actuator, 51: Second link plate, 52: Sixth link lever, 53: Seventh link lever, 54: Eighth link lever, 71: Shaft cap, 72: Bearing section, 81: Shaft, 90: Bearing section.

Claims

1. In an air conditioning system installed in a vehicle, Actuators (22, 50) and The first components (23-28, 51-54, 71, 72, 81, 90) that constitute part of the air conditioning system, The air conditioning system comprises a second component (23-28, 51-54, 71, 72, 81, 90) which forms part of the air conditioning system and slides with the first component when driven by the actuator, An air conditioning system in which the sliding part between the first part and the second part slides is configured such that the difference between the static friction coefficient and the kinetic friction coefficient in the sliding part (Δμ), the sliding speed of the sliding part when the actuator is driven (V), and the load acting on the sliding part (W) are set so that the stick-slip sound is below a predetermined volume that is not audible to the occupants.

2. The air conditioning device according to claim 1, wherein the first and second components are formed of a combination of materials such that, under the conditions of the sliding speed of the sliding part when the actuator is driven, and the conditions of the load acting on the sliding part, the difference between the static friction coefficient and the dynamic friction coefficient is smaller than the difference between the static friction coefficient and the dynamic friction coefficient that results in the stick-slip sound of a predetermined volume.

3. The air conditioning device according to claim 1 or 2, wherein one of the first and second parts is a part having grooves (31, 33, 34, 37, 42, 45, 57, 58, 64), and the other of the first and second parts is a part having pins (30, 35, 36, 40, 44, 46, 59, 62, 63) that slide inside the grooves, and the sliding part is formed by the grooves and the pins.

4. One of the first and second parts is formed of a highly sliding polyacetal, The air conditioning device according to claim 1 or 2, wherein the other of the first and second components is formed of polybutylene terephthalate.

5. The air conditioning device according to claim 1, wherein the load acting on the sliding part of the first part and the second part is set to be smaller than the load at which the stick-slip sound produces a predetermined volume, under the conditions of the difference between the static friction coefficient and the dynamic friction coefficient of the sliding part, and the sliding speed of the sliding part when the actuator is driven.

6. The air conditioning device according to claim 1, wherein, under the conditions of the difference between the static friction coefficient and the kinetic friction coefficient of the sliding part, and the sliding speed of the sliding part when the actuator is driven, the upper limit of the load acting on the sliding part is set to be less than the load at which the actuator locks and less than the load at which the stick-slip sound becomes the predetermined volume, and further, the lower limit of the load acting on the sliding part is set to be greater than the load at which the rattling sound between the first part and the second part becomes the volume at which the occupant cannot hear it.

7. The air conditioning device according to claim 5 or 6, wherein one of the first and second parts is a bearing portion (72, 90), the other of the first and second parts is a shaft (18, 71, 81) that slides inside the bearing portion, the sliding portion is formed by the bearing portion and the shaft, and the load acting on the sliding portion is adjusted by the shape of the bearing portion.

8. The air conditioning device according to claim 7, wherein the bearing portion (90) has a plurality of claw portions (94) that contact the outer circumferential surface of the shaft, and the shaft is held by the elastic force of the plurality of claw portions which are elastically deformable in a direction intersecting the axis (CL6) of the shaft.

9. The air conditioning device according to claim 8, wherein the holding force of the bearing portion in holding the shaft is adjusted by setting the number of claws of the bearing portion, the length of contact between the claws and the shaft, and the rigidity of the claws.

10. The air conditioning device according to claim 8, wherein the number of the aforementioned claws is four.

11. The air conditioning device according to claim 1, wherein the sliding speed of the sliding part of the first part and the second part during the operation of the actuator is set to be faster than the sliding speed at which the stick-slip sound becomes the predetermined volume, under the conditions of the difference between the static friction coefficient and the dynamic friction coefficient of the sliding part and the load acting on the sliding part.

12. The air conditioning device according to any one of claims 1, 2, 5, 6, or 11, wherein the sliding part is grease-free.

13. A method for manufacturing an air conditioning system mounted on a vehicle, comprising actuators (22, 50), first components (23-28, 51-54, 71, 72, 81, 90), and second components (23-28, 51-54, 71, 72, 81, 90) that slide with the first components when driven by the actuators, A method for manufacturing an air conditioning system, comprising setting the difference between the static friction coefficient and the kinetic friction coefficient (Δμ) in the sliding part where the first part and the second part slide against each other, the sliding speed (V) of the sliding part when the actuator is driven, and the load (W) acting on the sliding part, so that the stick-slip sound is at or below a predetermined volume that is inaudible to the occupants.

14. With respect to the first and second components, the method for manufacturing an air conditioning device according to claim 13, further comprising selecting a combination of materials such that, under the conditions of the sliding speed of the sliding part when the actuator is driven and the conditions of the load acting on the sliding part, the difference between the static friction coefficient and the dynamic friction coefficient is smaller than the difference between the static friction coefficient and the dynamic friction coefficient that results in the stick-slip sound of a predetermined volume.

15. A method for manufacturing an air conditioning device according to claim 13, wherein, with respect to the first and second components, the load acting on the sliding part is set to be smaller than the load on the sliding part at which the stick-slip sound produces a predetermined volume, under the conditions of the difference between the static friction coefficient and the dynamic friction coefficient of the sliding part and the sliding speed of the sliding part when the actuator is driven.

16. With respect to the first and second parts, the method for manufacturing an air conditioning device according to claim 13, wherein, under the conditions for the difference between the static friction coefficient and the dynamic friction coefficient of the sliding part and the sliding speed of the sliding part when the actuator is driven, the load acting on the sliding part is set as an upper limit to be less than the load at which the actuator locks and less than the load at which the stick-slip sound becomes the predetermined volume, and further, the load acting on the sliding part is set as a lower limit to be greater than the load at which the rattling sound between the first and second parts becomes the volume at which the occupant cannot hear it.

17. A method for manufacturing an air conditioning device according to claim 13, wherein, with respect to the first and second parts, the sliding speed of the sliding part during the operation of the actuator is set to be faster than the sliding speed at which the stick-slip sound produces a predetermined volume, under the conditions of the difference between the static friction coefficient and the dynamic friction coefficient of the sliding part and the load acting on the sliding part.

18. A method for manufacturing an air conditioning device according to any one of claims 13 to 17, wherein the sliding part is made grease-free.

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