JP2018135773A - refrigerator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To further suppress vibrations generated during the operation of a compressor.SOLUTION: A refrigerator has a supporting base 9 which is provided on a refrigerator body 3 and supports a compressor 7; a cushion rubber 13 which is provided between the compressor 7 and the supporting base 9, and is equipped with a cylinder portion 13p; and a supporting pin 15 which is attached to the supporting base 9 at a head portion 15a, and whose shaft portion 15b is inserted in the cylinder portion 13p. The cushion rubber 13 is provided with a projecting portion 13f which is easy to absorb vibrations generated during the operation of the compressor 7 as compared with the cylinder portion 13p, on an inner surface of the cylinder portion 13p so as to contact with an outer surface of the supporting pin 15.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a refrigerator in which a compressor is supported via an elastic member.

  The compressor provided in the refrigerator is supported via an elastic member such as rubber in order to suppress vibration propagation to the refrigerator main body during operation (see Patent Document 1). The elastic member of Patent Document 1 is designed to absorb vibrations by forming a lower portion in a bellows shape and providing a plurality of ribs radially between the upper and lower sides of the outer periphery.

JP 2001-59478 A

  However, due to recent improvements in heat insulation and energy-saving technology, low-capacity operation of compressors is required, and vibration suppression measures in a wider rotation range are required.

  Therefore, an object of the present invention is to further suppress vibrations generated during operation of the compressor.

  A refrigerator according to an embodiment of the present invention is provided in a refrigerator main body, and a support base that supports a compressor, an elastic member that is provided between the compressor and the support base, and includes a cylindrical portion, and the support base And a shaft member into which the shaft portion is inserted into the cylindrical portion of the elastic member. The elastic member is provided on the inner surface of the cylindrical portion such that a vibration absorbing portion that absorbs vibration generated during operation of the compressor more easily than the cylindrical portion is in contact with the outer surface of the shaft member. .

It is the perspective view seen from the back side of the refrigerator concerning the 1st Embodiment of the present invention. It is sectional drawing which shows the site | part periphery which attached the compressor of the refrigerator using cushion rubber. It is a perspective view of cushion rubber. It is a top view of cushion rubber. It is sectional drawing corresponding to FIG. 2 of 2nd Embodiment. It is a top view of cushion rubber of a 2nd embodiment. It is sectional drawing corresponding to FIG. 2 of 3rd Embodiment. It is a top view of cushion rubber of a 3rd embodiment. It is sectional drawing corresponding to FIG. 2 of 4th Embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  FIG. 1 shows the refrigerator 1 according to the first embodiment of the present invention as viewed from the back side. A machine room 5 is formed in the lower part of the back side of the refrigerator body 3, and a compressor is provided in the machine room 5. 7 is installed. The compressor 7 is mounted on a support base 9 located at the bottom of the machine room 5. The support base 9 is attached to the lower part of the side plate or the like of the refrigerator body 3 using bolts or the like. The compressor 7 is provided with a plate-like support leg 11 protruding in the horizontal direction at the lower part, and is attached to the support base 9 in a state where the support leg 11 is attached to a cushion rubber 13 as an elastic member. A plurality of support legs 11 are provided around the compressor 7.

  As shown in FIG. 2, the support base 9 has a bottom wall 9a, a lower side wall 9b, and an upper side wall 9c. Between the lower side wall 9b and the upper side wall 9c, the upper side of the lower side wall 9b is directed outward. And a step portion 9d that is bent in the horizontal direction and is connected to the upper side wall 9c. A recess 9e is formed in the vicinity of the lower side wall 9b of the bottom wall 9a, and the cushion rubber 13 is disposed in the recess 9e.

  A through hole 9eh is formed in the center of the recess 9e of the bottom wall 9a, and a support pin 15 as a shaft member is inserted into the through hole 9eh from below the bottom wall 9a. The support pin 15 includes a flat head portion 15a as a base portion and a shaft portion 15b having a smaller diameter than the head portion 15a. The head portion 15a is fixed to the concave portion 9e by welding in a state where the shaft portion 15b is inserted into the through hole 9eh.

  The shaft portion 15b includes a large-diameter portion 15b1 on the head 15a side and a small-diameter portion 15b2 on the distal end side that is longer in the axial direction than the large-diameter portion 15b1. The large diameter portion 15b1 and the small diameter portion 15b2 are connected by an inclined portion 15b3. The tip (upper end) of the shaft portion 15 b is located below the upper end of the upper side wall 9 c of the support base 9.

  An annular groove 15b4 is formed in the vicinity of the tip of the small diameter portion 15b2. A stopper member 17 made of a snap ring such as an E-shaped retaining ring is fitted in the groove 15b4. The stopper member 17 has a function of suppressing the support legs 11 of the compressor 7 from coming off from the support pins 15.

  Next, the cushion rubber 13 will be described in detail.

  The cushion rubber 13 is composed of substantially cylindrical EPDM (ethylene-propylene rubber) as a whole, and includes a through hole 13a into which the support pin 15 is inserted at the center. The support pin 15 inserted into the through hole 13a has a groove 15b4 located above the upper end surface 13b of the cushion rubber 13 and outside the through hole 13a. At this time, the upper end surface 13b of the cushion rubber 13 and the stopper member 17 are separated from each other.

  An annular support leg insertion groove 13 c into which the support leg 11 of the compressor 7 is fitted is formed in the vicinity of the lower side of the upper end surface 13 b of the cushion rubber 13. The support leg insertion groove 13c is formed between the flange portion 13d on the upper end surface 13b side and the flange portion 13e formed below the flange portion 13d. As shown in FIGS. 3 and 4, the flange portion 13 d and the flange portion 13 e are both circular when viewed from the axial direction of the support pin 15, and the outer diameter of the flange portion 13 d is smaller than the outer diameter of the flange portion 13 e.

  The shape of the inner surface of the through hole 13a changes along the axial direction of the support pin 15. The inner surface of the through hole 13a between the vicinity of the position corresponding to the support leg insertion groove 13c and the upper end surface 13b is provided with a convex portion 13f as a vibration absorbing portion. Four convex portions 13 f are provided at equal intervals along the circumferential direction of the support pin 15. As shown in FIG. 4, the convex portion 13 f has a substantially rectangular shape in plan view, and the tip end surface has a concave arc shape and is in close contact with the outer peripheral surface of the support pin 15.

  As shown in FIG. 4, between the four convex portions 13f is a substantially triangular concave portion 13g in plan view. A portion of the cushion rubber 13 excluding the substantially quadrangular convex portion 13f in plan view is a cylindrical portion 13p. That is, the cushion rubber 13 includes an outer cylindrical portion 13p and a convex portion 13f formed on the inner surface of the cylindrical portion 13p on the upper end surface 13b side.

  In the natural state shown in FIG. 3 and FIG. 4 before elastic deformation, the convex portion 13 f has an inner diameter of a circle formed by connecting four tip surfaces (arc surfaces), and the outer diameter of the small-diameter portion 15 b 2 of the support pin 15. Smaller than 0.5 mm. For this reason, the convex portion 13f is brought into surface contact with the distal end surface being pressed against the outer surface of the small diameter portion 15b2 of the support pin 15 in a state of being elastically deformed.

  The lower end portion of the cushion rubber 13 includes a circular substrate portion 13 h when viewed from the axial direction of the support pin 15. The substrate portion 13 h is placed in the recess 9 e of the bottom wall 9 a of the support base 9. The outer diameter of the substrate portion 13h is substantially the same as the outer diameter of the flange portion 13e. Therefore, the board | substrate part 13h is not visible in FIG. The thickness of the substrate portion 13h is about twice the thickness of the flange portion 13e.

  The inner surface of the through hole 13a at a position corresponding to the substrate portion 13h is provided with a protrusion 13i as a lower contact portion. Four protrusions 13i are provided at approximately equal intervals along the circumferential direction, and have a tapered mountain shape as shown in FIGS. As shown by the broken line in FIG. 4, the circumferential positions of the four protrusions 13i are the same as the circumferential positions of the four protrusions 13f. That is, the convex portion 13 f and the protrusion 13 i are in a position where they overlap when viewed from the axial direction of the support pin 15.

  In the natural state shown in FIG. 4 before the elastic deformation, the protrusion 13i has an inner diameter of a circle formed by connecting the four tips, which is about 0.5 mm smaller than the outer diameter of the large-diameter portion 15b1 of the support pin 15. . For this reason, the protrusion 13i is in an elastically deformed state so that the tip is pressed against the large diameter portion 15b1 of the support pin 15. At this time, the total contact area of the four protrusions 13f with respect to the small diameter portion 15b2 is larger than the total contact area of the four protrusions 13i with respect to the large diameter portion 15b1. That is, the protrusion 13i is pressed against and contacts the shaft portion 15b of the support pin 15 in a state closer to point contact than the convex portion 13f.

  As shown in FIG. 2, the cushion rubber 13 includes a bellows portion 13j having a wave shape along the axial direction between the flange portion 13e and the substrate portion 13h. The bellows portion 13j is provided with two curved portions 13j1 that are curved so as to protrude outward in the radial direction opposite to the support pin 15 along the axial direction.

  The inner surface of the through hole 13 a at a position corresponding to the bellows portion 13 j is separated from the shaft portion 15 b of the support pin 15. The inner surface of the through hole 13a at a position corresponding to the flange portion 13e is an inclined surface 13k that is spaced apart from the shaft portion 15b of the support pin 15 and expands outward from the upper side to the lower side. The vicinity of the lower portion of the inclined surface 13k becomes a cylindrical surface 13m having a constant inner diameter from the inclined surface 13k downward.

  Next, the function and effect will be described.

  Vibration generated during the operation of the compressor 7 is absorbed by the cushion rubber 13 and is suppressed from propagating to the housing of the refrigerator main body 3 via, for example, the discharge pipe 19 and the suction pipe 21 shown in FIG. If the compressor 7 here is inverter-controlled, for example, it operates in a wide rotational range. A large vibration is generated when the compressor 7 is rotating at high speed, and a small vibration is generated when the compressor 7 is rotating at low speed.

  Large vibrations are efficiently absorbed mainly by the cylindrical portion 13p including the bellows portion 13j that is elastically deformed vertically and horizontally. Small vibration is efficiently absorbed mainly by the convex portion 13f in contact with the shaft portion 15b being elastically deformed by being pressed against the shaft portion 15b in the radial direction. Even if some of the large vibrations could not be absorbed, some of the vibrations that could not be absorbed were transmitted from the bottom wall 9a to the installation surface (floor) where the refrigerator 1 is installed, and the casing of the refrigerator body 3 Propagation to can be suppressed.

  The present embodiment is provided in the refrigerator main body 3 and supports the compressor 7. The cushion base 13 provided between the compressor 7 and the support base 9 and provided with the cylindrical portion 13 p, and the support base 9. And a support pin 15 into which a shaft portion 15b is inserted into the cylindrical portion 13p. The cushion rubber 13 is provided on the inner surface of the cylindrical portion 13p so that a convex portion 13f that absorbs vibration generated during operation of the compressor 7 more easily than the cylindrical portion 13p is in contact with the outer surface of the support pin 15. .

  For this reason, small vibrations such as micro vibrations during operation in the lower rotation range of the compressor 7 can be efficiently absorbed by the convex portions 13f being pressed against the shaft portions 15b in the radial direction and elastically deforming. In particular, due to recent improvements in heat insulation and energy saving technology, low-capacity operation of the compressor is required, and the refrigerator 1 of the present embodiment can sufficiently meet this requirement. Further, it is not necessary to use an expensive material having a smaller elastic coefficient (easily elastically deformed) as the cushion rubber, and a cost reduction effect can be expected. As an example, the elastic modulus of EPDM used as the cushion rubber 13 may have a rebound resilience of 50 to 80%.

  The convex part 13f of the cushion rubber 13 of this embodiment is provided with two or more along the circumferential direction in the cylinder part 13p. For this reason, small vibrations such as micro vibration during operation in the lower rotation range of the compressor 7 can be more efficiently absorbed by the elastic deformation movement in the radial direction with respect to the shaft portion 15b of the plurality of convex portions 13f. it can.

  The plurality of convex portions 13 f of the present embodiment are in point-symmetric positions with respect to the axis of the support pin 15. For this reason, even if the direction of vibration by the compressor 7 is multidirectional with respect to the radial direction of the support pin 15, it can efficiently cope with it.

  The convex portion 13 f of the present embodiment is located on the cushion rubber 13. The cushion rubber 13 can more efficiently absorb small vibrations of the compressor 7 attached in the vicinity of the convex portion 13f by the convex portion 13f located at the upper portion.

  The cushion rubber 13 of the present embodiment includes a protrusion 13i that contacts the shaft portion 15b of the support pin 15 below the protrusion 13f, and the contact area of the protrusion 13f with the shaft portion 15b is relative to the shaft portion 15b of the protrusion 13i. Greater than contact area. Therefore, the protrusion 13f absorbs vibration more efficiently, avoids unnecessary contact with the support pin 15 by the lower protrusion 13i, and facilitates elastic deformation of the cushion rubber 13 particularly during large vibrations, thereby absorbing vibration. It becomes easy to do. The protrusion 13 i is provided mainly for positioning the cushion rubber 13 with respect to the support pin 15.

  The convex portion 13f of the present embodiment is in contact with the shaft portion 15b of the support pin 15 while being pressed. For this reason, the convex part 13f will contact reliably by the axial part 15b of the support pin 15, and a vibration absorption effect will increase more by elastic deformation movement.

  Next, a second embodiment of the cushion rubber will be described.

  As shown in FIGS. 5 and 6, the cushion rubber 13 </ b> A of the second embodiment is replaced with a buffer member 13 </ b> Af that is a separate member from the cylindrical portion 13 </ b> Ap, instead of the convex portion 13 f of the cushion rubber 13 of the first embodiment. Is provided as a vibration absorbing portion. The second embodiment is substantially the same as the first embodiment except that the buffer member 13Af is a separate member from the cylindrical portion 13Ap, and the same components are denoted by the same reference numerals. In addition, about the code | symbol of each part of cushion rubber | gum 13A, the capital letter "A" of the alphabet is added to the code | symbol of cushion rubber | gum 13 of 1st Embodiment.

  The buffer member 13Af is made of IIR (butyl rubber). The cylinder portion 13Ap of the cushion rubber 13A is made of EPDM (ethylene-propylene rubber), similarly to the cushion rubber 13 of the first embodiment. Since the buffer member 13Af made of IIR has a smaller elastic coefficient than the cylindrical portion 13Ap made of EPDM and is easily elastically deformed, it can absorb smaller vibrations. As an example, the IIR elastic modulus E1 may have a rebound resilience of 20 to 50%. The elastic modulus E2 of EPDM used as the cushion rubber 13 may have a rebound resilience of 50 to 80% as in the first embodiment. However, E1 <E2.

  The buffer member 13Af is provided from the upper end surface 13Ab of the cushion rubber 13A (cylindrical portion 13Ap) to a position substantially corresponding to the flange portion 13Ae, and as shown in FIG. 6, the convex portion of the cushion rubber 13 of the first embodiment. As with 13f, four are provided at equal intervals in the circumferential direction. The buffer member 13Af and the cylinder portion 13Ap are fixed in a state where the buffer member 13Af and the cylinder portion 13Ap are airtightly adhered with an adhesive, for example. Alternatively, after molding one of the buffer member 13Af and the cylinder portion 13Ap, the other may be integrally molded with respect to the other.

  The front end surface of the buffer member 13Af has a concave arc shape like the convex portion 13f, and is in close contact with the outer peripheral surface of the support pin 15. Further, in the natural state before elastically deforming the buffer member 13Af, the inner diameter of a circle formed by connecting the four tip surfaces is about 0.5 mm smaller than the outer diameter of the small diameter portion 15b2 of the support pin 15. For this reason, the buffer member 13Af is brought into elastic contact with the tip surface thereof being pressed against the outer surface of the small-diameter portion 15b2 of the support pin 15 to come into surface contact.

  Also in the second embodiment, small vibrations such as fine vibration during operation of the compressor 7 in a lower rotation range can be efficiently absorbed by the elastic deformation movement in the radial direction with respect to the shaft portion 15b of the buffer member 13Af. . In particular, due to recent improvements in heat insulation and energy-saving technology, low-capacity operation of the compressor is required, and the refrigerator of the second embodiment can sufficiently meet this requirement, and the same effects as in the first embodiment. Is obtained.

  In the cushion rubber 13A of the second embodiment, the buffer member 13Af is a separate member from the cylindrical portion 13Ap. Therefore, the cushion rubber 13A does not need to use a more expensive material (IIR) having a smaller elastic coefficient (easily elastically deformed) for the cylindrical portion 13Ap that occupies most of the cushion rubber 13A. IIR, which is more expensive than EPDM, is not used for the cylinder portion 13Ap but is used only for the buffer member 13Af, so that a cost reduction effect can be expected while enhancing the vibration absorption effect.

  Next, a third embodiment of the cushion rubber will be described.

  As shown in FIG. 7, the cushion rubber 13 </ b> B of the third embodiment is provided with a buffer member 13 </ b> Bf, which is a separate member from the cylinder portion 13 </ b> Bp, as a vibration absorbing portion, like the cushion rubber 13 </ b> A of the second embodiment. Yes. As shown in FIG. 8, the point which formed the buffer member 13Bf cyclically | annularly differs from 2nd Embodiment. Other configurations are substantially the same as those of the second embodiment, and the same components are denoted by the same reference numerals. In addition, about the code | symbol of each part of cushion rubber 13B, it replaces with the code | symbol "A" of cushion rubber 13A of 2nd Embodiment, and uses the capital letter "B" of the alphabet.

  Similar to the buffer member 13Af, the annular buffer member 13Bf is made of IIR (butyl rubber). The cylinder portion 13Bp of the cushion rubber 13B is made of EPDM (ethylene-propylene rubber), similarly to the cushion rubber 13 of the first embodiment. The buffer member 13Bf made of IIR has a smaller elastic coefficient than the cylindrical portion 13Bp made of EPDM and is easily elastically deformed, so that it can absorb smaller vibrations.

  The buffer member 13Bf is provided from the upper end surface 13Bb of the cushion rubber 13B (cylinder part 13Bp) to a position substantially corresponding to the flange part 13Be. The buffer member 13Bf and the cylinder portion 13Bp are fixed in a state where the buffer member 13Bf and the cylinder portion 13Bp are airtightly adhered with, for example, an adhesive. Alternatively, after molding one of the buffer member 13Bf and the cylinder portion 13Bp, the other may be integrally molded with respect to the other.

  The front end surface of the buffer member 13Bf has a concave arc shape like the convex portion 13f, and is in close contact with the outer peripheral surface of the support pin 15. Further, the buffer member 13Bf has an inner diameter in a natural state before being elastically deformed, which is about 0.5 mm smaller than an outer diameter of the small-diameter portion 15b2 of the support pin 15. For this reason, the buffer member 13Af is in an elastically deformed state, and the inner peripheral surface is pressed against the outer surface of the small diameter portion 15b2 of the support pin 15 to come into surface contact.

  Also in the third embodiment, small vibrations such as fine vibrations during operation of the compressor 7 in a lower rotation range can be efficiently absorbed by the elastic deformation movement in the radial direction with respect to the shaft portion 15b of the buffer member 13Bf. . In particular, due to recent improvements in heat insulation and energy-saving technology, low-capacity operation of the compressor is required, and the refrigerator of the third embodiment can sufficiently meet this requirement, and the same effects as in the second embodiment. Is obtained.

  The buffer member 13Bf of the third embodiment is formed in an annular shape. For this reason, the contact area of the buffer member 13Bf with respect to the support pin 15 is increased compared to the first and second embodiments with the axial length being equal, and the damping effect against small vibrations is enhanced. In addition, the same effects as those of the first and second embodiments can be obtained.

  FIG. 9 shows a cushion rubber 13C of the fourth embodiment. As in the second and third embodiments, the cushion rubber 13C is a member different from the cylinder portion 13Cp in which the buffer member 13Cf made of IIR is made of EPDM. The buffer member 13Cf has a longer axial length than the buffer member 13Af of the second embodiment or the buffer member 13Bf of the third embodiment. That is, the buffer member 13Cf is provided from the upper end surface 13Cb of the cushion rubber 13C (cylindrical portion 13Cp) to a position lower than the position corresponding to the flange portion 13Ce. Note that a plurality of buffer members 13Cf may be provided along the circumferential direction as shown in FIG. 6, or may be annular as shown in FIG.

  Other configurations of the fourth embodiment are substantially the same as those of the second and third embodiments, and the same components are denoted by the same reference numerals. In addition, about the code | symbol of each part of cushion rubber | gum 13C, it replaces with the code | symbol "A" and "B" of cushion rubber | gum 13A, 13B of 2nd, 3rd embodiment, and uses the capital letter "C" of the alphabet.

  In the cushion rubber 13C of the fourth embodiment, the contact area between the buffer member 13Cf and the support pin 15 is increased by increasing the axial length of the buffer member 13Cf in the second embodiment or the third embodiment. Larger than For this reason, the vibration damping effect becomes higher. In addition, the same effects as those of the second and third embodiments can be obtained.

  As mentioned above, although embodiment of this invention was described, these embodiment is only the illustration described in order to make an understanding of this invention easy, and this invention is not limited to the said embodiment. The technical scope of the present invention is not limited to the specific technical matters disclosed in the above embodiment, but includes various modifications, changes, alternative techniques, and the like that can be easily derived therefrom.

  For example, in the first embodiment, the cushion rubber 13 is made of EPDM, but synthetic rubber other than EPDM may be used. The cushion rubbers 13A, 13B, and 13C of the second to fourth embodiments have the cylindrical portions 13Ap, 13Bp, and 13Cp made of EPDM. However, synthetic rubber other than EPDM may be used, and the cushioning member 13Af, Although 13Bf and 13Cf are made of IIR, synthetic rubbers other than IIR may be used. However, it is assumed that the buffer members 13Af, 13Bf, and 13Cf have a smaller elastic coefficient than the cylindrical portions 13Ap, 13Bp, and 13Cp.

  The convex portion 13f of the first embodiment and the buffer members 13Af, 13Bf, and 13Cf of the second to fourth embodiments are provided at four locations in the circumferential direction, but are not limited to four locations.

  Similarly to the buffer member 13Cf of the fourth embodiment, the convex portion 13f of the first embodiment may have a longer axial length. That is, you may provide the convex part 13f to the position corresponding to the inclined surface 13k and cylindrical surface 13m of FIG.

DESCRIPTION OF SYMBOLS 1 Refrigerator 3 Refrigerator main body 7 Compressor 9 Refrigerator main body support base 13, 13A, 13B, 13C Cushion rubber (elastic member)
13p, 13Ap, 13Bp, 13Cp Cushion rubber cylinder part 13f Cushion rubber convex part (vibration absorbing part)
13Af, 13Bf, 13Cf Cushion rubber cushioning member (vibration absorbing part)
13i Cushion rubber protrusion (downward contact)
15 Support pin (shaft member)
15a Support pin head (base)
15b Shaft part of support pin

Claims (8)

A support base provided in the refrigerator body and supporting the compressor;
An elastic member provided between the compressor and the support base and provided with a cylindrical portion;
A base member attached to the support base, and a shaft member into which a shaft portion is inserted into the cylindrical portion of the elastic member;
The elastic member is provided on the inner surface of the cylindrical portion such that a vibration absorbing portion that absorbs vibration generated during operation of the compressor more easily than the cylindrical portion is in contact with the outer surface of the shaft member. A refrigerator characterized by that.   The refrigerator according to claim 1, wherein a plurality of the vibration absorbing portions are provided along a circumferential direction of the cylindrical portion of the elastic member.   3. The refrigerator according to claim 2, wherein the plurality of vibration absorbing portions are in a point-symmetric position with respect to an axis of the shaft member.   The refrigerator according to any one of claims 1 to 3, wherein the vibration absorbing portion is located above the elastic member.   The elastic member includes a lower contact portion that contacts the shaft portion of the shaft member below the vibration absorbing portion, and a contact area of the vibration absorbing portion with respect to the shaft portion is relative to the shaft portion of the lower contact portion. The refrigerator according to claim 4, wherein the refrigerator is larger than a contact area.   The refrigerator according to any one of claims 1 to 5, wherein the vibration absorbing portion is in contact with the shaft portion being pressed against the shaft portion.   The refrigerator according to claim 1, wherein the vibration absorbing portion is a separate member with respect to the cylindrical portion.   The refrigerator according to claim 7, wherein the vibration absorbing portion is formed in an annular shape.

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