Skin treatment device

Abstract

The utility model provides a skin treatment device which can set the temperature of a contact surface in contact with a skin surface to be more than 20 DEG C lower than the ambient air temperature so as to improve the comfort of skin treatment. The skin treatment device is provided with a contact component and a skin treatment component, wherein the contact component is provided with a contact surface contacted with a target object; a heat absorbing member configured to absorb heat from the contact member; and a heat dissipating member configured to dissipate the heat absorbed by the heat absorbing member, the contact member further including an opposing surface opposing the contact surface, and a side surface constituting a surface from one end of the contact surface to one end of the opposing surface, and when a substantial total area of the contact surface, the opposing surface, and the side surface is expressed as A square meters, A square meters are less than A square meters. Configuration # imgabs0 # when the substantial height of the contact surface is expressed in L metres and the amount of heat absorbed by the heat absorbing member is expressed in Qc watts

Description

Technical Field

[0001] The present utility model relates to a skin treatment device for performing hair removal treatment and the like. Background Art

[0002] Conventionally, as a traditional skin treatment device, a device has been proposed in which the contact surface temperature of the surface in contact with the skin of the person to be treated (user) is set lower than the air temperature. The purpose is to relieve the pain and the like generated in the person to be treated (user) due to irradiation with laser or the like.

[0003] Prior Art Documents:

[0004] Patent Document 1: Japanese Unexamined Patent Application Publication No. 2018-61727 Summary of the Utility Model

[0005] However, compared with traditional skin treatment devices, there is a need to set the contact surface temperature of the surface in contact with the skin lower to further promote the relief of pain and the like generated due to irradiation with laser or the like.

[0006] Therefore, the present utility model aims to provide a skin treatment device that can set the contact surface temperature of the surface in contact with the skin to be more than 20 degrees lower than the surrounding air temperature, thereby improving the comfort of skin treatment.

[0007] In one aspect, in order to achieve the above object, the present utility model provides the following solutions.

[0008] (1) The present utility model provides a skin treatment device, comprising: a contact member having a contact surface that contacts a target object; a heat absorption member configured to absorb heat from the contact member; and a heat dissipation member configured to dissipate the heat absorbed by the heat absorption member. The contact member further includes: a relative surface opposite to the contact surface, and a side surface forming a surface from one end of the contact surface to one end of the relative surface. When the substantial total area of the contact surface, the relative surface, and the side surface is represented by A square meters, the substantial height of the contact surface is represented by L meters, and the heat absorption amount of the heat absorption member is represented by Qc watts, it is configured that (heat absorption amount Qc / (heat transfer area A × 2.51 × 0.56)) ^ 0.8 × height L ^ 0.2 exceeds 20.

[0009] (2) In the configuration of (1) above, it further includes a main body housing, the main body housing includes the contact member, and at least one of the relative surface and the side surface is a structure held via the main body housing and a heat insulation member.

[0010] (3) In the configuration of (2) above, the heat conduction coefficient of the heat insulation member is less than the heat conduction coefficient of the contact member.

[0011] (4) In the configuration of (2) above, it includes: the heat absorption member that requires heat supply of Qd watts when generating heat absorption of Qc watts, fins that form part of the heat dissipation member, a air supply member that blows air to the fins, and an exhaust port provided in a part of the main body housing. When the surface area of the fins is represented by AF square meters, the effective air flow length of the fins is represented by LF meters, and the wind speed discharged from the exhaust port is represented by V m / s, it is configured such that (Qc + Qd) / (3.86 × √(V / LF) × AF) is less than 10.

[0012] (5) In the configuration of (4) above, the air supply member includes an air inlet and an air outlet, and the air outlet is disposed opposite to the fins.

[0013] (6) In the configuration of (5) above, the heat dissipation member includes: a first cooling part that receives the air blown out from the air outlet, and a second cooling part that receives the air inhaled from the air inlet.

[0014] The effects of the utility model are as follows.

[0015] According to the present utility model, the contact surface temperature in contact with the skin surface can be set to be more than 20 degrees lower than the surrounding air temperature, thereby improving the comfort of skin treatment. Description of the Drawings

[0016] Figure 1 is an external perspective view of the hair removal device of this embodiment.

[0017] Figure 2 (a) is a partial cross-sectional perspective view of the hair removal device of this embodiment, and (b) is a side view of the sapphire glass and the Peltier element.

[0018] Figure 3 (a) is an exploded perspective view of the fan and the heat sink, and (b) is an exploded perspective view of the fan and the heat sink observed from different angles.

[0019] Figure 4 is an oblique view of machine A.

[0020] Figure 5 is a perspective view of machine B.

[0021] Figure 6 is a diagram summarizing the improvement plan, concerns, and improvement suggestions of machine A.

[0022] Figure 7 is a diagram showing the evaluation results of the influence degree of each component of machine A and machine B and their combinations on the temperature of the sapphire glass.

[0023] Figure 8 It is a diagram showing the temperature drop values of sapphire glass in each component of Machine A and Machine B and their combinations.

[0024] Figure 9 It is a characteristic curve graph of the heat absorption amount with respect to the current value of the Peltier element.

[0025] Figure 10 It is an explanatory diagram for explaining the calculation of coefficient C.

[0026] Figure 11 It is a characteristic curve graph of the heat absorption amount with respect to the current value of the Peltier element.

[0027] Figure 12 It is a diagram showing the values of each part on the heat dissipation side of Machine A and Machine B.

[0028] Figure 13 It is an explanatory diagram for explaining heat transfer.

[0029] Figure 14 It is a diagram showing the temperature difference when various heat conductive pads are used on the heat absorption side of Machine B.

[0030] Figure 15 It is a diagram showing the evaluation of the theoretical calculation technology, parameter design technology, and simulation technology of Machine A and Machine B.

[0031] In the figure: 1 - hair removal device (skin treatment device), 2 - sapphire glass (contact component), 2a - contact surface, 2b - opposite surface, 2c - side surface, 3 - Peltier element (heat absorption component), 4 - heat sink (heat dissipation component), 4A - first cooling part, 4B - second cooling part, 4a - fin, 5 - fan (air supply component), 5a - air intake, 10 - main body housing, 10b - exhaust port. Detailed Embodiments

[0032] Hereinafter, based on the drawings, the embodiments of the present utility model will be described in detail.

[0033] As Figures 1 to 3 shown, the hair removal device 1 as a skin treatment device includes a sapphire glass 2 as a contact component, a Peltier element 3 as a heat absorption component that absorbs heat from the sapphire glass 2, a heat sink 4 as a heat dissipation component that dissipates the heat absorbed by the Peltier element 3, a fan 5 as an air supply component that supplies air to the heat sink 4, a laser irradiation unit 6, a power supply unit 7, and a main body housing 10 that houses these components (except for a part of the sapphire glass 2).

[0034] Sapphire glass 2 is a material with high thermal conductivity and is housed in the main body housing 10 in a state where the contact surface 2a in contact with the target skin surface is exposed to the outside. The sapphire glass 2 is a flat cuboid and includes a contact surface 2a, an opposite surface 2b opposite to the contact surface 2a, and a side surface 2c extending from one end of the contact surface 2a to one end of the opposite surface 2b. When the actual total area of the contact surface 2a, the opposite surface 2b, and the side surface 2c is represented by A square meters, the actual height of the contact surface 2a is represented by L meters, and the heat absorption amount is represented by Qc watts, when the temperature difference between the surrounding air temperature (for example, room temperature) and the surface temperature of the sapphire glass 2 is represented by the surface temperature difference ΔTs of the sapphire glass 2, the surface temperature difference ΔTs of the sapphire glass 2 can be represented by the following formula.

[0035] The surface temperature difference ΔTs of the sapphire glass 2 = (heat absorption amount Qc / (heat transfer area A × 2.51 × 0.56))^0.8 × height L^0.2, and is configured such that the surface temperature difference ΔTs exceeds 20. The lower limit value of the low temperature is set to a temperature that can prevent low temperature burns (for example, ΔTs = 50).

[0036] All four side surfaces of the sapphire glass 2 are held in the main body housing 10 together by a heat insulating member 11 and sealed air (not shown) as heat insulating members. The heat insulating member 11 is, for example, a foam plastic material. The thermal conductivity of the heat insulating member 11 is set to be less than the thermal conductivity of the sapphire glass 2.

[0037] When the Peltier element 3 generates a heat absorption amount of Qc watts, Qd watts are required as the heat supply amount. Heat conductive pads (not shown) are respectively used for the electrodes on the heat absorption side and the heat dissipation side of the Peltier element 3.

[0038] The heat sink 4 is preferably formed of a sheet metal copper material. The thermal conductivity of the sheet metal copper material is 398 (W / mK). Since its thermal conductivity is superior to that of the aluminum material, the device can be miniaturized. The heat sink 4 includes a first cooling part 4A that receives the wind blown out from the air outlet 5b (described below) of the fan 5 and a second cooling part 4B that receives the wind inhaled from the air inlet 5a of the fan 5 (as Figure 3 shown). The first cooling part 4A and the second cooling part 4B each include a plurality of fins 4a arranged at intervals, and the first cooling part 4A and the second cooling part 4B are separated by a partition 4b to prevent the wind from flowing between them.

[0039] The fan 5 includes an air inlet 5a (as Figure 3 shown) and an air outlet 5b (as Figure 3 shown). The air outlet 5b is arranged opposite to the fins 4a of the first cooling part 4A so as to supply air to the fins 4a of the first cooling part 4A. More specifically, the fan is configured such that the wind can smoothly flow into the gap space between the plurality of fins 4a.

[0040] The surface area of the fin 4a is expressed in square meters as AF, the effective air flow length of the fin 4a is expressed in meters as LF, the wind speed discharged from the exhaust port 10b below is expressed in meters per second as V, the heat generated by the Peltier element 3 is expressed as Qc, the heat required to supply the Peltier element 3 to generate Qc is expressed as Qd, and when the temperature difference between the surrounding air temperature and the surface temperature of the fin 4a is expressed as the surface temperature difference ΔTh of the heat sink 4, the surface temperature difference ΔTh of the heat sink 4 is represented by the following approximate formula of the heat transfer coefficient (heat transfer coefficient) of forced convection.

[0041] The surface temperature difference ΔTh of the heat sink 4 = (Qc + Qd) / (3.86×√(V / LF)×AF), and ΔTh is set not to exceed 10.

[0042] The main body housing 10 has a rectangular parallelepiped shape. On one side of the main body housing 10, there are provided a plurality of air intake ports 10a for the fan 5 to suck air and a plurality of air exhaust ports 10b for the fan 5 to discharge air. On the other side of the main body housing 10, there are provided a plurality of air exhaust ports 10c for the discharged air to pass through the laser irradiation unit 6 and the power supply unit 7.

[0043] The laser irradiation unit 6 is composed of a laser light source, an output circuit unit of the laser light source, a reflecting plate surrounding the laser light source, and the like.

[0044] As described above, the skin treatment device of the present utility model includes: a sapphire glass 2 including a contact surface 2a that contacts the skin surface, a Peltier element 3 that absorbs heat from the sapphire glass 2, and a heat sink 4 that dissipates the heat absorbed by the Peltier element 3, and is set such that the surface temperature difference ΔTs of the sapphire glass 2 (that is, the difference between the surface temperature of the sapphire glass 2 and the surrounding air temperature (for example, room temperature)) exceeds 20 degrees. Therefore, the surface temperature of the sapphire glass 2 is 20 degrees or more lower than the surrounding air temperature (for example, room temperature), and the person to be treated (user) can feel sufficient coolness when contacting the sapphire glass 2, thereby improving the comfort of skin treatment during laser irradiation.

[0045] Including a Peltier element 3 that requires a supply of heat Qd watts to generate a heat absorption amount Qc watts, a plurality of fins 4a constituting the heat sink 4, a fan 5 that blows (supplies air) to the fins 4a, and an exhaust port 10b disposed in a part of the main body housing 10, when the surface area of the fin 4a is expressed in square meters as AF, the effective air flow length of the fin 4a is expressed in meters as LF, and the wind speed discharged from the exhaust port 10b is expressed in meters per second as V, when (the surface temperature of the heat sink - room temperature) is expressed as the surface temperature difference ΔTh of the heat sink 4, the formula ΔTh = (Qc + Qd) / (3.86×√(V / LF)×AF) is formed, and ΔTh is set not to exceed 10. Therefore, the surface temperature of the fin 4a is only less than 10 degrees higher than the surrounding air temperature (for example, room temperature), thereby achieving sufficient heat dissipation.

[0046] The heat sink 4 includes a first cooling portion 4A that receives the air blown out from the air outlet 5b of the fan 5 and a second cooling portion 4B that receives the air sucked in from the air inlet 5a of the fan 5. Accordingly, the second cooling portion 4B is disposed in the air passage from the air inlet 10a of the main body housing 10 to the air inlet 5a of the fan 5, thereby expanding the heat dissipation area of the fins 4a of the heat sink 4, improving the heat dissipation performance, and effectively utilizing the space.

[0047] All side surfaces 2c of the sapphire glass 2 are held in the main body housing 10 by the heat insulating member 11 serving as a heat insulating member and the sealed air (not labeled). Accordingly, it is possible to greatly prevent the cooling heat of the sapphire glass 2 from radiating (blowing) to the main body housing 10. In the present embodiment, all side surfaces 2c of the sapphire glass 2 are held in the main body housing 10 by the heat insulating member 11 serving as a heat insulating member and the sealed air, but it is also possible to hold at least one of the opposite surfaces 2b and the side surfaces 2c of the sapphire glass 2 in the main body housing 10 only by the heat insulating member. The heat insulating member 11 is, for example, a foam plastic.

[0048] In addition, although it is described that the heat insulating member is made of a foam plastic, it is not limited thereto, and it may be other foam resins or foam rubbers. By surrounding the contact member with a foam rubber, in addition to heat insulation, it is possible to improve the airtightness and reduce the phenomenon of internal condensation due to cooling. Although the light source is described as a laser, it is not limited thereto, and it may be an LED or an IPL light source. Particularly in the case of an IPL light source, it is possible to alleviate the pain caused by instantaneous light emission by cooling the sapphire glass, thereby increasing the emission energy of the IPL and improving the effects such as hair removal.

[0049] Furthermore, although the contact member is described by taking the sapphire glass as an example, it is not limited thereto, and a filter that partially cuts off the light wavelength may also be provided. In this way, the desired light effect can be obtained. In the above description, although it is described that the Peltier element is used for cooling, it is not limited thereto, and by connecting the heat direction in the opposite direction, it is possible to heat the contact member, that is, collect heat from the air, recover it through the copper plate fins, absorb it on the Peltier element, and dissipate the heat to the contact member. In this way, it is possible to increase blood flow, etc. by heating, and thus effective skin treatment can be performed.

[0050] Next, the experiments and theories that led to the above-described embodiment of the hair removal device 1 will be described. As the experimental machines, Machine A shown in Figure 4 and Machine B shown in Figure 5 were used. The conclusion is that in order to set the surface temperature of the sapphire glass 2 to be more than 20 degrees below room temperature, it was found through comparative evaluation and theoretical calculation that the following problems need to be solved.

[0051] Countermeasure Plan 1: Increase the current of the Peltier element 3 to improve the cooling effect and increase the heat absorption to more than 3.2 W.

[0052] Countermeasure Plan 2: Reduce the heat transfer area of the sapphire glass 2 to 994 mm 2 .

[0053] Countermeasure Plan 3: Increase the wind speed inside the heat sink (cooling part) to more than 7 m / s and increase the heat transfer coefficient (heat transfer rate) to 60 W / m 2 K.

[0054] Countermeasure Plan 4: Re-evaluate the material of the heat sink 4 and control the temperature difference between the heat dissipation side of the Peltier element 3 and the fin 4a below 5 K.

[0055] Countermeasure Plan 5: Increase the fin surface area to 23,136 mm 2 .

[0056] Countermeasure Plan 6: Select a thermal conductive pad with a high thermal conductivity λ and a small (thin) thickness dx.

[0057] Below, the reasons leading to these conclusions are explained.

[0058] When considering the countermeasure plans for Machine A, the Figure 6 shown concerns and improvement measures were proposed.

[0059] In Machine A and Machine B, a comparative experiment on the temperature of the sapphire glass 2 was conducted, and the contribution degree of each design parameter was analyzed. As a result, the Figure 7 shown evaluation results and the Figure 8 shown results of the reduction ΔT in the surface temperature of the sapphire glass were obtained.

[0060] That is to say, regarding the surface temperature of the sapphire glass 2, the configuration of the fan 5 and the size of the sapphire glass 2 have a greater impact, and other impacts are smaller. Therefore, it is most necessary to improve the parameters with a greater impact.

[0061] Regarding the Peltier element 3, the surface temperature of the sapphire glass 2 in Machine A is lower, but this is because the heat generated by the Peltier element 3 is less. In addition, it was also found that the influence of the component combination is very large. Simply changing the current value of the Peltier element 3 is not enough, and it is also necessary to re-evaluate the size and cooling structure of the sapphire glass 2.

[0062] First, the improvement of the heat absorption side is explained.

[0063] When the difference between the ambient air temperature (e.g., room temperature) and the surface temperature of the sapphire glass 2 is expressed as the surface temperature difference ΔTs of the sapphire glass 2, the surface temperature difference ΔTs of the sapphire glass 2 = (heat absorption Qc / (heat transfer area A × 2.51 × coefficient C))^0.8 × height L^0.2. Therefore, for machine B, the countermeasure plan 1 is: increase the current of the Peltier element 3 to improve the cooling effect and increase the heat absorption to more than 3.2 W; the countermeasure plan 2 is: reduce the heat transfer area of the sapphire glass 2 to 994 mm 2 .

[0064] According to Figure 9 the chart shown, when the current value of the Peltier element 3 is approximately 0.9, the heat absorption Qc of machine B can reach 3.2 W.

[0065] For the heat transfer area A of the sapphire glass 2 of machine B, if the glass size is WHD = 30 × 11 × 15 (mm), the total area of the front, back, left, and right sides can be set to 0.0009944 m 2 (= 994 mm 2 ). The height L (H) in the above formula is 11 mm. For the heat transfer area A of the sapphire glass 2 of machine A, if the glass size is WHD = 32 × 32.6 × 3 (mm), the total area of the front, back, left, and right sides is 0.002282 m 2 . The height L (H) in the above formula is 32.6 mm.

[0066] As Figure 10 shown, the value of the coefficient C for both machine A and machine B is 0.56.

[0067] Accordingly, the results shown in Figure 8 are obtained on the heat absorption side.

[0068] Next, the improvement on the heat dissipation side will be described.

[0069] Since the wind (air) of the fan 5 does not effectively flow to the heat sink 4 and the surface area of the heat sink 4 is small, improvement (modification) is required. According to the approximate formula for the heat transfer coefficient of forced convection, the heat transfer coefficient = 3.86 × √(wind speed V inside the heat sink (cooling part) / fin length LF). The radiant heat is ignored. Therefore, for machine B, the countermeasure plan 3 is: increase the wind speed inside the heat sink to more than 7 m / s and increase the heat transfer coefficient to 60 W / m 2 K (the experimental result is 59.5 W / m 2 K).

[0070] The heat release amount Qh = thermal conductivity × (the surface temperature of the heat sink (cooling part) - room temperature) × surface area. Therefore, countermeasure plan 4 is taken: re-evaluate the material of the heat sink 4, control the temperature difference between the heat dissipation side (heat release side) of the Peltier element 3 and the fin 4a to be below 5K, and take countermeasure plan 5: increase the fin surface area to 23,136 mm 2 .

[0071] Here, the surface area of the fin 4a is expressed in square meters as AF, the effective air flow length of the fin 4a is expressed in meters as LF, the wind speed discharged from the exhaust port 10b is expressed in meters per second as V, the heat generated by the Peltier element 3 is expressed as Qc, the heat required to supply the Peltier element 3 to generate Qc is expressed as Qd, and when (the surface temperature of the heat sink - room temperature) is expressed as the surface temperature difference ΔTh of the heat sink 4, the formula ΔTh = (Qc + Qd) / (3.86 × √(V / LF) × AF) is formed. If the value of the surface temperature difference ΔTh of the heat sink 4 can be set to be small, a good heat dissipation performance structure can be obtained.

[0072] Since the current value supplied to the Peltier element 3 is 0.9, therefore according to Figure 11 , the heat release amount Qh of machine B is approximately 13.8, and the heat release amount Qh of machine A is approximately 6.0.

[0073] In machine A, the structure of the heat sink 4 is composed of 18 fins 4a with dimensions of 15.3 mm × 18 mm arranged at intervals. Machine A can only utilize 15% of the individual wind speed of the fan 5. The surface temperature of the heat sink 4 is higher than that of machine B, and the cooling effect is insufficient.

[0074] In machine B, the structure of the heat sink 4 is composed of 27 fins 4a with dimensions of 20.5 mm × 20.9 mm arranged at intervals. Machine B can utilize 80% of the individual wind speed of the fan 5. The wind speed inside the heat sink (cooling part) is 6.4 times that of machine A, the thermal conductivity is 2.3 times that of machine A, the fin surface area is 2.3 times that of machine A, and the heat release amount is 2.3 times that of machine A.

[0075] Thus, the results shown in Figure 12 are obtained on the heat release side.

[0076] Next, the selection of the temperature gradient and the thermal pad will be described.

[0077] If Q: heat passing through (W), A: cross-sectional area, λ: thermal conductivity, dx: pad thickness (distance), then the temperature difference dt = -(Q / A) × (dx / λ). The heat passing through (heat flux) Q is based on Figure 13 as Q = A·λ·(Th - Tc) / dx. Among them, Th is the surface temperature and Tc is the temperature after passing through.

[0078] Therefore, countermeasure plan 6 was adopted: select a thermal pad with a high thermal conductivity λ and a thin thickness dx. Thermal pads with a thermal conductivity λ of 12 W / mK or 6 W / mK and a pad thickness of 1 mm or 2 mm were used on the heat-absorbing side of machine B, and the temperature difference dt was measured. Figure 14 The results are shown.

[0079] From Figure 14 it can be seen that even when using thermal pads with different thermal conductivities λ and pad thicknesses dx, the heat absorption Qc and heat release Qh of the Peltier element 3 hardly change, so the effect is limited.

[0080] In summary, as Figure 15 shown, there are doubts about the data of machine A in theoretical calculations, parameter design, and the application of simulation technology, but the data of machine B is available in theoretical calculations, parameter design, and simulation technology. Therefore, by developing a structure that can ensure the required heat absorption and heat dissipation performance, it is possible to obtain the conclusion of realizing a skin treatment device that can set the contact surface temperature in contact with the skin surface to be more than 20 degrees lower than the surrounding air temperature (room temperature).

[0081] The embodiments have been described in detail above, but the present utility model is not limited to specific embodiments, and various deformations and modifications can be made within the scope described in the scope of the patent technical solution. In addition, all or multiple constituent elements of the foregoing embodiments can also be combined.

[0082] Additional Notes

[0083] (Additional Note 1)

[0084] (1) The skin treatment device of the present utility model includes: a contact member having a contact surface in contact with a target; a heat-absorbing member configured to absorb heat from the contact member; and a heat-dissipating member configured to dissipate the heat absorbed by the heat-absorbing member. The contact member further includes: a relative surface opposite to the contact surface, and a side surface forming a surface from one end of the contact surface to one end of the relative surface. When the substantial total area of the contact surface, the relative surface, and the side surface is represented by A square meters, the substantial height of the contact surface is represented by L meters, and the heat absorption of the heat-absorbing member is represented by Qc watts, it is configured that (heat absorption Qc / (heat transfer area A × 2.51 × 0.56))^0.8 × height L^0.2 exceeds 20.

[0085] (2) In the configuration of (1) above, a main body housing is further included, the main body housing includes the contact member, and at least one of the relative surface and the side surface is a structure held via the main body housing and a heat-insulating member.

[0086] (3) In the configuration of (2) above, the heat transfer coefficient of the heat insulation member is less than the heat transfer coefficient of the contact member.

[0087] (4) In the configuration of (2) above, it includes: the heat absorption member that requires heat Qd watts to be supplied when generating heat absorption Qc watts, fins that form a part of the heat dissipation member, a air supply member that blows air onto the fins, and an exhaust port provided in a part of the main body housing. When the surface area of the fins is represented by AF square meters, the effective air flow length of the fins is represented by LF meters, and the wind speed discharged from the exhaust port is represented by V m / s, it is configured such that (Qc + Qd) / (3.86 × √(V / LF) × AF) is less than 10.

[0088] (5) In the configuration of (4) above, the air supply member includes an air inlet and an air outlet, and the air outlet is disposed opposite to the fins.

[0089] (6) In the configuration of (5) above, the heat dissipation member includes: a first cooling part that receives the air blown from the air outlet, and a second cooling part that receives the air inhaled from the air inlet.

Claims

1. A skin treatment device, characterized in that: have: a contact member having a contact surface for contacting a target object; a heat absorbing member configured to absorb heat from the contact component; as well as a heat dissipation member configured to dissipate the heat absorbed by the heat absorption member; The contact member further includes an opposing surface opposing the contact surface, and a side surface constituting a surface from one end of the contact surface to one end of the opposing surface. When the substantial total area of ​​the contact surface, the opposing surface and the side surface is represented by A square meters, the substantial height of the contact surface is represented by L meters, and the heat absorption capacity of the heat absorption member is represented by Qc watts, it is constituted as follows: More than 20.

2. The skin treatment device according to claim 1, characterized in that A main body casing is also included, the main body casing includes the contact member, and at least one of the opposing surface and the side surface is a structure held via the main body casing and a heat insulating member.

3. The skin treatment device according to claim 2, characterized in that: The thermal conductivity of the thermal insulation member is smaller than the thermal conductivity of the contact part.

4. The skin treatment device according to claim 2, characterized in that: include: The heat absorbing member that needs to supply heat Qd watt when generating the absorbed heat Qc watt, the fins that constitute a part of the heat dissipating member, the air supply member that blows air toward the fins, and the exhaust port provided in a part of the main body shell, When the surface area of ​​the fin is represented by AF square meters, the effective wind flow length of the fin is represented by LF meters, and the wind speed discharged from the exhaust port is represented by V meters / second, it is composed of Less than 10.

5. The skin treatment device according to claim 4, characterized in that: The air supply component includes an air inlet and an air outlet, and the air outlet is arranged opposite to the fin.

6. The skin treatment device according to claim 5, characterized in that: The heat dissipation member includes: a first cooling portion that receives the wind blown out from the air outlet; and A second cooling unit receives the air sucked from the air intake port.

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