JP2008000194A - Washing/drying machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent vibration of a fan device for circulation/blowing from being propagated to a heat pump mechanism or leaking out as noise. <P>SOLUTION: The washing/drying machine comprises the heat pump mechanism composed of a circulation pathway for circulation/blowing and a compressor with an evaporator and a heat-exchange unit 28 of a condenser disposed on the way of the circulation pathway, etc., and the fan device 34 connected to the heat-exchange unit 28 for circulating air inside the circulation pathway. The washing/drying machine also has a boss 43 with small diameter at a position facing the fan device 34 side or the heat-exchange unit 28 side, and a hollow cylindrical part 45 with large diameter at a position facing the other side as connection means for the fan device 34 and the heat-exchange unit 28. A cylindrical vibration-proofing member 46 with a projection 50 on the outer surface is interposed in the fitted part of the boss and the hollow cylindrical part. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a washing and drying machine provided with a fan device that heats air using a heat pump mechanism during a drying operation and circulates and blows air inside the circulation path.

  Conventionally, as this type of washer-dryer, for example, a drum-type washer / dryer is provided with a rotatable drum for storing clothes in a water tank that can store water, and a washing process such as washing, rinsing, and dehydration, and a drying process are performed. It can be operated automatically or selectively. In order to increase the efficiency of heat energy used for drying, particularly in the drying process, hot air heated to a predetermined temperature can be circulated and supplied into the drum. For this purpose, a circulation path connected to the inlet and outlet of the hot air before and after the water tank is formed, and a heating means and an air blowing means for warming air are provided in the middle of the circulation path so that air (warm air) is used. The drying operation is performed in a closed loop circuit without discharging to the outside, and the living environment where the washing and drying machine is installed can be comfortably executed without being affected by the temperature and humidity due to the exhaust.

  However, in recent years, it has been proposed to adopt a heat pump mechanism as a heating means in place of a conventional electric heater to obtain a more efficient drying action. As is well known, this consists of a refrigeration cycle in which a refrigerant is circulated in the order of a condenser, a capillary tube, and an evaporator by means of a compressor. A condenser is provided and a fan device for circulating air is interposed (see, for example, Patent Document 1).

  In general, the heavy heat pump mechanism is attached and fixed to the bottom of the washing and drying machine main body, and a fan device is provided so as to be connected and fixed thereto. Therefore, the vibration caused by the driving of the fan device during the drying operation is also transmitted to the heat pump mechanism, which extends to the bottom of the main body, and causes deterioration of vibration and noise. Therefore, as a mounting means of this type of fan device, it is usually configured to be screwed via a vibration isolating member such as rubber (see, for example, Patent Documents 2 and 3).

FIG. 10 shows a conventional configuration based on the above-mentioned Patent Document 2. The fan 1 is mounted and fixed by screwing a screw 1c into the fan bracket 2 through a grommet 1a and a collar 1b. As a result, vibration generated while the fan 1 is rotationally driven can be attenuated by the grommet 1a, while the collar 1b can suppress the deformation amount of the grommet 1a to a constant amount.
JP 7-178289 A Japanese Utility Model Publication No. 5-59000 JP-A-6-74491

  However, according to the above configuration, the state in which the grommet 1a is locally compressed between the collar 1b due to the weight of the fan 1 continues (the portion indicated by the compression portion P in the drawing), and the vicinity of the compression portion P eventually undergoes plastic deformation. Thus, the elasticity is lost and the desired vibration-proofing effect cannot be obtained by so-called dynamic spring hardening. Therefore, the vibration from the fan 1 is transmitted to the fan bracket 2 side through the hardened portion of the grommet 1a, the collar 1b, and the screw 1c, so that vibration and noise are generated outside the machine.

  In order to solve the above problems, the present invention is provided with a vibration-proof member that does not cause dynamic spring hardening due to the weight load of the fan device, and is capable of expecting a long-term vibration-proofing effect and washing and drying that can eliminate noise problems. The purpose is to provide a machine.

  In order to achieve the above object, a washing and drying machine of the present invention includes a water tank having a rotating tub for storing laundry, a circulation path provided in communication with the water tank, and a circulation path of the circulation path. A heat pump mechanism comprising a compressor or the like in which a heat exchange unit of an evaporator and a condenser is arranged in the middle, and a fan device connected to the heat exchange unit and circulating air in the circulation path, the fan device and the The connection means with the heat exchange unit consists of one small boss provided at the opposite position from the fan device side and the heat exchange unit side, the other large hollow cylindrical portion, and the outer periphery of these fitting portions. A cylindrical vibration-proof member having a convex portion on the surface is interposed.

  According to the above means, vibration from the fan device can be prevented from being transmitted to the heat exchanging unit side by the vibration isolating member, and the own weight of the fan device is received by the convex portion of the vibration isolating member, and dynamic spring hardening is prevented. Even if it occurs, only a part of the protrusion is stopped, and the vibration isolator can still provide an effective vibration damping effect over a long period of time.

(First embodiment)
1 to 6 show a first embodiment of the present invention applied to a drum-type washing / drying machine. First, an overall configuration of the washing / drying machine will be schematically described with reference to FIGS. However, FIG. 2 is a longitudinal side view of the washing / drying machine, and FIG. 3 is a perspective view of the state where the back cover is removed. In particular, as shown in FIG. 2, the main body 11 forming the outer shell of the washing / drying machine is provided with a door 12 for opening and closing the laundry input opening on the front side, and a base plate 13 having support legs 13a on the bottom. And a back cover 14 that is detachable on the rear side. In the main body 11, a water tank 15 capable of storing water elastically supported by a plurality of suspensions 21 which are dynamic vibration absorption systems is provided. In the water tank 15, a drum 16 which is a rotating tank rotates around an inclined horizontal axis. Both are provided so as to be opposed to the door 12 (laundry input port).

  As is well known, the drum 16 has a large number of small holes 16a in the peripheral wall and an annular liquid balancer 17 that is a dynamic vibration absorbing system at the open end. On the other hand, the water tank 15 includes an annular water tank cover 18 attached to the opening end portion thereof, and covers the front surface portion having the balancer 17 of the drum 16. And between the front-end | tip part of this water tank cover 18, the back surface of the said door 12, and the laundry input port, the flexible bellows 19 is provided watertight, and scattering of the water from the water tank 15 outside, etc. are carried out. I try to prevent it. The drum 16 is directly driven to rotate by an outer rotor type DC brushless motor 20 provided on the back side of the water tank 15.

  An air circulation path 29 is formed outside the water tank 15 and connected to a suction port 22a and a blow-out port 24a provided in the front and rear portions of the water tank 15, respectively. That is, on the front side, a part of the water tank cover 9 is used to integrally form the exhaust duct 22 that constitutes the circulation path 29. The exhaust duct 22 is formed in a hollow cylindrical shape, and a plurality of suction ports 22a are formed on two inner surfaces of the upper portion thereof, and the other end is suspended downward. On the other hand, the outlet 24a is formed in the rear surface side of the water tank 15, the air supply duct 24 is connected to this, and the other end is suspended downward. The air outlet 24a communicates with an air vent 25 formed on the rear surface of the drum 16 facing the air outlet 24a, and can supply air (hot air to be described later) into the drum 16.

In this way, the supply and exhaust ducts 24 and 22 are formed outside the water tank 15, and the hanging ends of the supply and exhaust ducts 24 and 22 are installed on the base plate 13 via the expansion joints 26 and 27 (details will be described later). Thus, an air circulation path 29 through the water tank 15 is configured.
However, the heat exchange unit 28 will be described in detail. The base plate 13 which is the bottom of the main body 11 is provided with a heavy heat pump mechanism 30. As is well known, this heat pump mechanism 30 is configured by a refrigeration cycle in which refrigerant is circulated in the order of a condenser 31, a capillary tube (throttle) (not shown), and an evaporator 32 when a compressor (not shown) is driven. In particular, the condenser 31 that is driven during the drying operation heats the air, and the evaporator 32 exhibits a so-called heat exchange function that cools the air and condenses moisture in the air.

  Thus, the condenser 31 and the evaporator 32 are disposed in the lower heat exchange duct 33 of which the circulation path 29 is configured, and a heat exchange action is performed between the air flowing in the duct 33. It is configured as a so-called heat exchange unit 28. Accordingly, the right and left ends of the heat exchange duct 33 constituting the heat exchange unit 28 are connected to the expansion joints 26 and 27, respectively, but a fan device 34 for circulating the air in the circulation path 29 is provided. The heat exchange unit 28 (heat exchange duct 33) is connected and fixed to the right side in FIG. 2 (details will be described later), and is therefore connected to the expansion joint 27 via the fan device 34. It becomes the structure connected to the duct 24 in communication.

  In FIG. 1, a drain hose 23 connected to the bottom of the water tank 15 can be drained to the outside through a drain valve (not shown), and the heat exchange duct 33 is so-called cooled and condensed by the evaporator 32. A drainage means (not shown) for draining dehumidified water is provided, and of course, a water supply means such as a water supply valve (not shown) for supplying water into the water tank 15 is provided in the upper part of the main body 11. ing.

  Here, the connection fixing means between the heat exchange unit 28 and the fan device 34 for circulating air will be described in particular with reference to FIGS. 1 and 4 to 6. First, the configuration of the fan device 34 will be outlined. FIG. 4 shows a plan view of the fan device 34 connected and fixed to the heat exchange unit 28, and FIG. 5 shows a case cover 35b of the fan case 35 (see FIG. 4). The front view of the state which removed is shown.

  However, FIG. 5 shows a configuration in which the blower fan 36 is arranged in the case body 35a of the spiral container, and the fan is rotated by a fan motor (not shown) and blows in the direction of arrow A. Accordingly, a circulating air flow that flows in the direction of arrow A is generated in the circulation path 29 shown in FIG. The blower fan 36 is a blower in the circulation passage 29 having a large air passage resistance, and thus a turbo fan having a high static pressure is particularly suitable, but a sirocco fan can also be used. And the groove part 37 is formed in the outer periphery of this case main body 35a, and when not closing with the case cover 35b, the packing which is not illustrated is interposed and it is set as the watertight structure.

  In addition, mounting holes 38 projecting in a boss shape are provided on the outer peripheral wall of the case main body 35a at appropriate intervals, for example, a total of eight locations, which are fastened with screws 39 as shown in FIG. It is for fixing. Further, for example, at four locations on the outer peripheral wall of the case main body 35a, mounting arms 40 having an L-shaped cross section are provided to project outward. The mounting arm 40 is configured such that the fan device 34 is fastened and fixed to the heat exchange unit 28 by, for example, a tapping screw 41 via the mounting arm 40 as shown in FIG. The outlet 41 is attached upward and is connected in communication with the above-described air supply duct 24 side (see FIG. 2).

  The specific fixing means for the fan device 34 and the heat exchange unit 28 will be described with reference to FIG. FIG. 1 is an enlarged view of a main portion of a fastening portion by a tapping screw 41 via the mounting arm 40 described above, in which FIG. 1 (a) is an external view and FIG. 1 (b) is a cross-sectional view. Show. First, when connecting the fan device 34 and the heat exchange unit 28, specifically, the fan case 35 of the fan device 34 is joined to the end plate 33a of the heat exchange duct 33 on the heat exchange unit 28 side as shown in the figure. In this case, although not shown in the drawing, the air is circulated as a matter of course, and therefore, a bonding structure is provided between both of them to prevent air leakage.

  In this embodiment, a cylindrical boss 43 protrudes integrally in the horizontal direction on the end plate 33 a of the heat exchange duct 33 of the heat exchange unit 28. The boss 43 is made of metal and is provided corresponding to the mounting arm 40, and thus is provided at four locations, and has a mounting hole 43a at the center so that the tapping screw 41 can be screwed therein. On the other hand, the arm portion 44 extending outward is projected from the mounting arm 40, and an insertion hole 44a is formed in the arm portion 44. The diameter is far larger than the outer diameter of the tapping screw 41 through which the insertion portion 44 is inserted. It has a large circular shape. A cylindrical hollow tube portion 45 is provided integrally with the insertion hole 44a so as to protrude from the arm portion 44 to the left in the drawing. The inner diameter D1 of the hollow cylindrical portion 45 is larger than the outer diameter D2 of the boss 43 (D1> D2). Therefore, the boss 43 has a sufficient clearance inside the hollow cylindrical portion 45, that is, so-called idle. It is set as the structure which can be fitted in a state.

  However, an anti-vibration member 46 shown in FIG. 6 is interposed between the fitting parts of the boss 43 and the hollow cylinder part 45 in the loose state. FIG. 6A is a perspective view of the vibration isolation member 46, and FIG. 6B shows a cross-sectional view. First, the vibration-proof member 46 will be described. The vibration-proof member 46 is made of an elastic material such as rubber or resin and has a vibration-damping action, and is formed in a cylindrical shape as a whole. On the inside thereof, stepped holes having different diameters are continuously formed. A large-diameter fitting portion 47 is provided on the left side of the figure, and a small-diameter insertion portion 48 is provided on the right side. The fitting portion 47 can be fitted with the boss 43 (details will be described later), and the insertion portion 48 has a diameter that allows the tapping screw 41 to be inserted.

  On the other hand, on the outer peripheral surface of the vibration isolating member 46, a plurality of convex portions 50 project from the outer peripheral surface of the large-diameter cylindrical portion 49 corresponding to the fitting portion 47. . The convex portion 50 has, for example, a shape projecting linearly with a parallel interval in the circumferential direction. On the other hand, the right half has a small diameter as a whole and forms a constricted portion 51 which is in the outer periphery of the insertion portion 48 and is partially recessed in an annular shape. Therefore, also on the outer peripheral surface of the vibration isolating member 46, the cylindrical portion 49 side and the constricted portion 51 side have a stepped shape having substantially different outer diameter dimensions.

  The anti-vibration member 46 having such a configuration is interposed between the mounting arm 40 and the boss 43 as shown in FIG. As a specific assembling procedure, the cylindrical portion 49 side that forms a large-diameter outer peripheral surface by the convex portion 50 is elastically inserted into the hollow cylindrical portion 45 protruding from the arm portion 44, and at the same time the constricted portion 51. Is inserted to a position where it engages with the insertion hole 44 a of the arm portion 44.

  At this time, the arm portion 44 by the constricted portion 51 is engaged in the loose insertion state. That is, the tip of the constricted portion 51 is press-fitted with a diameter larger than that of the insertion hole 44a, but the peripheral surface after insertion and the insertion hole 44a are in a loose insertion state having a radial gap α shown in the figure, and Engage in the retaining state. The loose insertion state having the gap α is maintained even in a state of being fastened and fixed by a tapping screw 41 described later. On the other hand, the cylindrical portion 49 is completely accommodated in the hollow cylindrical portion 45 of the mounting arm 40, and accordingly, the convex portion 50 on the outer peripheral surface thereof is accommodated in a pressure contact state with the inner surface of the hollow cylindrical portion 45.

  As described above, the bosses 43 are fitted to the fitting portions 47 of the vibration isolating member 46 attached to the attachment arm 40 at four positions corresponding to the fitting portions 47 without any gaps. In this case, as described above, a packing (not shown) is interposed between the end plate 33a of the heat exchange duct 33 and the fan case 35 so as to be joined in an airtight state. As a result, the fan device 34 and the heat exchange unit 28 are connected via the vibration isolation member 46, and the circulation path 29 is also connected in a communicating state.

  In this state, the tapping screw 41 is inserted from the insertion portion 48 of the vibration isolating member 46 and fastened to the mounting hole 43a of the boss 43, thereby fixing the connection state. If an excessive tightening force is applied at the time of fastening of the tapping screw 41, there is a possibility that the loosening state of the clearance α may not be maintained by compressing the vibration damping member 46, particularly the constricted portion 51 side. The force is made constant so that the vibration isolating member 46 is not compressed more than necessary, and is always fastened and fixed with the clearance α secured.

Next, the operation of the drum type washing / drying machine having the above configuration will be described.
In the drum type washing and drying machine, when a standard driving course is selected and set and the operation is started, the speed of the drum 16 containing the laundry is controlled by a control device (not shown) as is well known, and washing, rinsing, dehydration and drying are performed. Each stroke is performed automatically. Note that the vibration accompanying the rotation of the drum 16 is subjected to vibration damping action and load balance adjustment by the suspension 21 and the liquid balancer 17 which are dynamic vibration absorbing systems, and vibration transmission to the main body 11 side is effectively suppressed.

  Thus, the drying process in which the heat pump mechanism 30 functions will be described. The drum 16 containing the laundry is rotated at a low speed, and the fan device 34 is driven. As a result, circulating air in the direction of arrow A shown in FIG. 2 is generated in the circulation path 29, and the air exchanges heat through the heat exchange unit 28 of the heat pump mechanism 30 disposed in the middle of the circulation path 29. Is done.

  In other words, the air is heated by the condenser 31 and warmed to reach the air supply duct 24 through the fan device 34 (fan case 35) and the expansion joint 27, and from the outlet 24a of the water tank 15 to the drum 16 through the vent 25. Supplied in. The warm air comes into contact with the laundry in the drum 16 to take away moisture, and thus a drying action is performed. The warm air (exhaust air) after contributing to drying flows into the exhaust duct 22 from the suction port 22a on the front side as air containing a lot of moisture, and reaches the heat exchange duct 33 through the expansion joint 26. Then, the air is cooled in the evaporator 32 and the moisture is condensed and dehumidified. The dehumidified air is heated again in the condenser 31 to be regenerated as warm air, supplied into the drum 16 and used for the drying action. It is repeatedly performed.

  By the way, the heat exchange unit 28 having the evaporator 32 and the condenser 31 arranged in the heat exchange duct 33 is installed on the base plate 13 which is the bottom of the main body 11. A fan device 34 is connected and fixed to one end of the heat exchange unit 28 in a communicating state. Therefore, when the blower fan 36 is rotationally driven, the vibration is immediately transmitted to the heat exchange unit 28 and is generated outside the main body 11 together with noise. In particular, in the heat exchange duct 33 that constitutes a part of the closed space of the circulation path 29, vibration is likely to be generated and transmitted. However, in this embodiment, as disclosed in FIG. 1 in particular, the vibration isolating member 46 is interposed between the mounting arm 40 on the fan device 34 side and the boss 43 on the heat exchange unit 28 side. Is attenuated and noise can be prevented.

  In addition, as a specific configuration, even if the insertion hole 44a of the arm portion 44 and the constricted portion 51 are engaged with each other by preventing the slippage (lateral direction), there is always a gap α in the radial direction. The weight in the direction is not directly burdened and therefore no direct vibration transmission is performed, at least the vibration transmission is greatly reduced. On the other hand, in the cylindrical portion 49 and the plurality of convex portions 50 that are fitted into the boss 43 and whose outer peripheral surface is in pressure contact with the hollow cylindrical portion 45, the convex portion 50 can reduce the weight or vibration of the fan device 34. In addition to elastically receiving and effectively exhibiting a damping effect, the vibration-proofing action of the cylindrical portion 49 itself can be sufficiently exhibited to effectively prevent generation of vibration and noise.

  In addition, in a part of the plurality of convex portions 50 that are always subjected to a weight burden from the upper part in long-term use, the elastic spring is hardened due to deformation caused by local pressure and loss of the original elasticity. The anti-vibration effect cannot be exhibited, and vibration may be transmitted from the cured portion. However, even if a part of the convex part 50 causes dynamic spring hardening as in the present embodiment, it only stops at a part of the convex part 50 and does not reach the cylindrical part 49. Therefore, the anti-vibration effect by the other convex portions 50 can still be effectively exhibited against the tendency to be transmitted from the surroundings like vibration, and the anti-vibration effect by the cylindrical portion 49 itself is not reduced at all. Can be used effectively.

According to the said Example, there exist the following effects.
Since the anti-vibration member 46 is interposed and fixed between the connection portions of the heat exchange unit 28 and the circulation blower fan device 34 interposed in the middle of the circulation path 29, rotational vibration of the blower fan 36 and the like are caused. It is not transmitted to the heat exchange unit 28 side, and noise generation outside the main body 11 can be effectively prevented.

  Moreover, in the conventional vibration isolating member, there is a risk that dynamic spring hardening occurs due to compression by a heavy load over a long period of time, and the original vibration isolating function may be lost. Since the weight load of the fan device 34 is elastically supported by the plurality of convex portions 50 protruding from the outer peripheral surface 49, even if the dynamic spring is cured by long-term use, a part of the convex portion 50 is formed. Therefore, the contact area is extremely small, and there is no possibility that the cylindrical portion 49 on the inner peripheral side is cured. In addition, the vibration damping effect by the other protrusions 50 is effective, and naturally the vibration damping effect of the entire vibration isolation member 46 can be expected. For example, it is effective for preventing vibration transmission over a long period of time and effective for preventing noise generation. is there. Therefore, vibration generated from the fan device 34 side is not transmitted to the heat exchange unit 28 side, and vibration transmission to the main body 11 and noise are not generated outside through the installed base plate 13.

  Further, in this embodiment, a constricted portion 51 is provided which is effective for preventing the vibration isolating member 46 from coming off, and an assembling work into the fan case 35 and a fastening work using a tapping screw 41 to the boss 43 are facilitated. Since the peripheral surface of 51 is engaged with the other side (arm portion 44) and the lateral direction which is the withdrawal direction in a state having a clearance α, the constricted portion 51 is subjected to a weight load from above. There is no effect. Therefore, dynamic spring hardening does not occur in the constricted portion 51, and vibration transmission can be effectively avoided by the gap α.

  7 to 9 show the second to third embodiments with respect to the above-described embodiment. Hereinafter, substantially the same parts as those in the above-described embodiment will be denoted by the same reference numerals, and description thereof will be omitted. I will explain each part.

(Second Embodiment)
First, FIG. 7 shows a second embodiment of the present invention, which is equivalent to FIG. This is a structure in which a cylindrical collar 52 is inserted into the vibration isolating member 46, and the tapping screw 41 is inserted through the collar 52. Except for the structure employing the collar 52, the structure is substantially the same as the above embodiment. In common.
That is, the collar 52 has a rigid cylindrical shape, has an outer diameter that is substantially the same as the inner peripheral surface of the insertion portion 48 of the vibration isolation member 46, and has an inner diameter that allows the tapping screw 41 to be inserted. The shape is slightly shorter than the length of 48.

  Therefore, as an assembling procedure in the present embodiment, the collar 52 is inserted into the insertion portion 48 after the vibration-proof member 46 is elastically attached to the mounting arm 40 of the fan case 35. The remaining work is the same as in the above embodiment. This is because, for example, in the vibration isolating member 46 in which the collar 52 is inserted first, the collar 52 hinders the flexibility of the constricted portion 51, so that the collar 52 is elastically inserted into the insertion hole 44 a of the arm portion 44 and engaged. It can be understood from the fact that it cannot be held.

  However, as shown in FIG. 7B, the inner end of the inserted collar 52 is stopped by the boss 43, so that the length of the collar 52 is slightly shorter than the insertion portion 48 (in the drawing). (Indicated by dimension S). In other words, the right end portion of the vibration isolation member 46 slightly protrudes from the collar 52. For this reason, when the tapping screw 41 is finally inserted and screwed to the boss 43, the dimension S corresponds to a certain tightening allowance of the vibration isolation member 46. Therefore, for example, there is no risk that the vibration damping member 46 is compressed to a predetermined level or more by being tightened too much to be cured in a tension state and the vibration damping effect is reduced.

  According to such a configuration, in addition to the effects of the above-described embodiment, the collar 52 is inserted into the vibration isolation member 46, whereby the tightening allowance of the vibration isolation member 46 by the tapping screw 41 can be made constant, and the vibration isolation function can be stabilized. Thus, the reliability of the quality can be increased, and the fastening operation of the tapping screw 41 can be easily performed.

(Third embodiment)
8 and 9 show the third embodiment, which corresponds to FIGS. 1 and 6, respectively.
This is a vibration isolation member 54 having a collar 53 in addition to the collar 52 in the second embodiment, and the rest of the configuration is the same as in the above embodiment. Thus, as clearly shown in FIG. 9, the vibration isolator 54 in the present embodiment is integrally formed with a disc-shaped flange 53 extending outward on the outer periphery of the left end portion on the large-diameter fitting portion 47 side. Is.
Accordingly, as is apparent from the assembled form shown in FIG. 8, the flange 53 formed at the outer end is an assembled configuration that does not require assembly adjustment with other members, and is the same as the second embodiment. The fan device 34 can be connected and fixed to the heat exchange unit 28 by an assembling procedure.

  By the way, in the anti-vibration member 46 of the above-mentioned embodiment which does not have this flange part 53, after attaching this anti-vibration member 46 to the attachment arm 40, as an assembly procedure for fitting the boss 43 to the fitting part 47 without a gap. As described above. However, due to the fact that the anti-vibration member 46 has a large sliding resistance with the boss 43 with respect to a material such as rubber, as the boss 43 is inserted, the left end of the anti-vibration member 46 on the inlet side (tubular shape) Part 49) was involved. Naturally, this also affects the background conditions such as the material of the cylindrical portion 49 and the protrusion 50 on the left end side being flexible and having a large frictional force, and the thickness of the cylindrical portion 49 being relatively thin and being easily caught. ing.

  Therefore, in the vibration isolating member 54 of the present embodiment, a disc-shaped flange portion 53 that extends outward is integrally formed at the left end portion of the cylindrical portion 49. Accordingly, the insertion of the boss 43 and the pulling action of the left end portion that pulls the cylindrical portion 49, the friction with the boss 43 according to the flange portion 53 that extends in a substantially perpendicular direction to the cylindrical portion 49 and forms a disk shape. Sufficient resistance can be obtained to prevent the cylindrical portion 49 from being caught by force. As a result, as shown in FIG. 8B, the intended cylindrical portion 49 and the convex portion 50 are interposed between the hollow cylindrical portion 45 (inner diameter D1) and the boss 43 (outer diameter D2) in an appropriate state. In addition to the expected anti-vibration effect, it can be incorporated without fear of being caught, improving workability and stabilizing the quality.

  The present invention is not limited to the embodiment described above and shown in the drawings. For example, the convex portion protruding from the outer peripheral surface of the vibration isolating member may be spiral instead of linear or linear. It is good also as a shape projected instead of dot shape instead of. Moreover, what is necessary is just a so-called attachment screw including not only a tapping screw but a general screw, a volt | bolt, etc. In addition, the rotating tank is not limited to the drum configuration around the horizontal axis, and can be used in a washing / drying machine equipped with a washing and dehydrating tank around the vertical axis, as well as the specific configuration of the circulation path and the flow direction of the circulating air. Various modifications can be made without departing from the scope of the present invention.

The principal part of 1st Example which applied this invention to the drum type washing-drying machine is expanded and shown, (a) External view, (b) The sectional drawing Longitudinal side view showing the overall structure of the washing and drying machine Disassembled perspective view with back cover removed Top view of the fan unit Front view of the fan unit with the case lid removed (A) external perspective view and (b) cross-sectional view of the vibration isolator FIG. 1 equivalent view showing the second embodiment FIG. 1 equivalent view showing the third embodiment 6 equivalent diagram Sectional view of the main part showing a conventional example

Explanation of symbols

  In the drawings, 11 is a main body, 15 is a water tank, 16 is a drum (rotary tank), 28 is a heat exchange unit, 29 is a circulation path, 30 is a heat pump mechanism, 31 is a condenser, 32 is an evaporator, and 33 is a heat exchange duct. , 34 is a fan device, 35 is a fan case, 35a is a case body, 35b is a case lid, 36 is a blower fan, 40 is an attachment arm, 41 is a tapping screw (attachment screw), 43 is a boss, 44 is an arm portion, 46, 54 is a vibration isolating member, 49 is a cylindrical part, 50 is a convex part, 51 is a constricted part, 52 is a collar, and 53 is a collar part.

Claims (3)

A compressor in which a water tank having a rotating tub for storing laundry is provided in the main body, a circulation path provided in communication with the water tank, and a heat exchange unit for an evaporator and a condenser in the circulation path A heat pump mechanism composed of, etc., and a fan device connected to the heat exchange unit and circulating air in the circulation path,
The connecting means between the fan device and the heat exchange unit includes one small-diameter boss provided at the opposite position from the fan device side and the heat exchange unit side, the other large-diameter hollow tube portion, and these A washer-dryer characterized in that a cylindrical vibration-proof member having a convex portion on the outer peripheral surface is interposed in the fitting portion.   The washing / drying machine according to claim 1, wherein a rigid and cylindrical collar is inserted into the vibration isolating member, and a mounting screw is fastened to the boss through the collar.   The washing / drying machine according to claim 1 or 2, wherein the vibration-proof member is formed with a flange portion protruding outward at a cylindrical end portion on a side where the boss is inserted.

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