JP4712679B2 - Heat pump equipment - Google Patents

Description

  The present invention relates to a damping structure for reducing vibration and noise of a heat pump device (including a refrigerator) in which a compressor is installed on a frame.

  A conventional heat pump device has, for example, at least a compressor, a refrigerant pipe, a heat exchanger, and a support member that supports them as described in Patent Document 1, and as a compressor of such a heat pump device, For example, when using a screw compressor having at least a gate rotor and a screw rotor as disclosed in Patent Document 2, or a screw compressor having at least a male and female rotor as disclosed in Patent Document 3, For example, by installing a vibration isolating mechanism as disclosed in Patent Document 4 between a compressor foot and a support member, a vibration isolating mechanism or a spring or rubber sheet or an elastomer resin or / and a combination thereof. , Suppresses transmission of vibrations generated from the compressor to the support member, and reduces noise caused by resonance of the support member. Raw was not suppressed. In general, anti-vibration rubber is often used rather than the stalk, which is because the surging phenomenon is remarkable.

  In general, a heat pump apparatus having such a screw compressor is large, and the overall dimensions of the apparatus are a width of 1500 to 10000 mm, a depth of 500 to 3000 mm, and a height of about 1500 to 3000 mm. In addition to the weight of the compressor being several hundred kg, the piping, the heat exchanger, and the control box are also heavy, and there are an air heat exchanger, a blower, etc., and the weight of the entire apparatus is 1 t or more. Therefore, in such a heat pump apparatus, it is common to install a frame that supports the entire apparatus from below.

  Such a frame needs to have a large section modulus in order to support heavy objects, such as Japanese Industrial Standard JIS-G3350 “Lightweight shape steel for general structure” and JIS-G3192 “Shape of hot rolled shape steel, Using a fastening part such as a bolt, nut, rivet, etc., with a frame having a cross-sectional shape, as described in JIS-G3466 "Square steel pipe for general structure" or similar. Or it is common to install in the frame of the substantially rectangular structure formed by combining by welding via the support frame for supporting the heavy article connected to a frame.

  In such a heat pump apparatus, the compressor is generally mounted on the frame, and the fastening portion between the compressor and the frame does not directly transmit the vibration generated from the compressor to the frame from the compressor foot. As described above, an anti-vibration rubber is installed between the compressor foot and the underframe. The anti-vibration rubber is shaped like a mount-type anti-vibration rubber as disclosed in Patent Document 4, for example, and a sheet-like anti-vibration rubber or ridge is installed between the base frame and the compressor foot. In general, a bolt for fixing the compressor to the underframe passes through the underframe, the compressor foot, and the anti-vibration rubber and is fastened and fixed with a nut. In addition, the cross-sectional shape of the underframe is a U-shape having an upper flange and a lower flange that extend in the horizontal direction on the top and bottom of the vertical portion, in order to stably fix and install the anti-vibration rubber and the compressor foot, The upper flange and the lower flange have a thickness of about several mm to several tens of mm, and have a width substantially equal to or larger than the width and depth of the compressor foot.

  Moreover, the oscillation frequency of a screw compressor used in such a heat pump device is generally several hundred Hz, and in particular, there are many examples in which the oscillation occurs in the vicinity of 300 Hz.

Japanese Patent Laying-Open No. 2003-56930 (FIG. 1, pages 4-5) JP 2001-182680 A (FIG. 1, page 3) Japanese Patent No. 2945526 (FIG. 1, page 2) JP-A-5-287087 (FIGS. 1-5 and 3-5)

  As described above, the cross-sectional structure of the underframe on which the compressor is installed has an upper flange and a lower flange that extend outward in the horizontal direction above and below the vertical portion, and the compressor is compressed on the flat portion of the upper flange. Put on your feet. The flat part of the upper flange is, for example, a roughly rectangular shape with a width of about 100 mm and a depth of about 1000 to 2000 mm when a compressor with a weight of several hundred kg is placed, and the plate thickness of the flange part is several mm, and the material is mild steel Often used as a steel material.

  On the other hand, the natural vibration of the rectangular flat plate when the vertical portions of the four sides of the rectangle are assumed to be the support ends is generally obtained by the following equation (1), and the infinite number of natural frequencies is obtained by changing the orders of m and n. I understand that it exists.

  When the above formula (1) is applied to the flat portion of the flange, it can be seen that a large number of natural frequencies exist in the range of 100 to 2000 Hz within the range of the dimensions and the plate thickness. Due to the presence of the natural frequency, it is difficult to avoid resonance with respect to the oscillation frequency of the screw compressor and its second and third harmonics.

  In general, the above formula (1) is applied to the case of a four-side support end, and the natural vibration is predicted by a commercially available finite element method program for more accurate prediction. For example, assuming that the above rectangular shape is made by bending a steel plate with a width of 75 mm, a height of 150 mm, a depth of 1750 mm, and a plate thickness of 4.5 mm at the outer R9 mm, the outer shell shape is formed by the SHELL element. When the natural frequency is calculated using a computer by the finite element method under the condition that the elements are divided by a mesh of about 10 mm and both side edges in the depth direction are completely fixed, 107, 136, 270, 276, 295, 318, 354, 367, 399, 400, 421, 451, 494, 509, 544, 573, 583, 594, 635, 644, 661, 702, 722, 755, 767, 806, 837, 863, 896, 915, 964, 993, 999, 1015, 1025, 1075, 1091, 1097 Hz, not several Hz There are natural frequency every several tens Hz, became innumerable result of the presence of the natural frequency in the range of more than this frequency. In this calculation, US ANSYS Inc. A general purpose finite element method program ANSYS Ver 8.0 was used.

  When the cross-sectional shape is a shape in which a bent part (lip) is provided at the open end of the U-shaped horizontal flange, or when the open end of the U-shaped (lip) is the bottom surface, etc. Even if it is changed, the natural frequency slightly changes, but there are many natural vibrations, and the tendency that the natural frequency exists near the oscillation frequency and the second and third harmonics of the compressor does not change.

  As described above, when the screw compressor is supported by a frame having a simple cross-sectional structure, it is found that it is difficult to avoid resonance of the frame even if the cross-sectional shape is changed.

  As a method for avoiding resonance without changing the basic structure of the cross section, it is conceivable to reduce the width of the plane portion. In the above equation (1), it can be seen that if the variable a is reduced, the influence of the order m increases, and the generated density of the natural frequency decreases when the order m is changed. For the same reason, it is estimated that the appearance density of the natural frequency of the plane portion also decreases.

  However, in order to stably support a compressor having a weight of several hundred kg, the width and height of at least 50 mm or more are required as the cross-sectional shape of the underframe, and if the width of the flat portion is 50 mm or more, screw compression is required. It is difficult to design a structure that avoids resonance by removing the natural vibrations of the frame and the plane from the machine's oscillation frequency and second and third harmonics.

  In addition, when it is difficult to avoid resonance of the underframe, there is a method of suppressing vibration transmission by installing an anti-vibration rubber or ridge having a sufficiently low spring constant between the compressor foot and the flat portion. In this method, the lower the spring constant theoretically, that is, the softer the vibration transmission to the flat part is suppressed, but conversely, the compressor itself is not fixed and the vibration amplitude of the compressor itself is increased. The vibration is transmitted to the refrigerant pipe, the pipe vibration increases, the support frame that fixes the pipe also vibrates, the noise due to the vibration of the pipe and the support frame increases, and the expected noise reduction effect cannot be obtained. There are drawbacks. In order to improve this point, it is necessary to give flexibility to the refrigerant piping connected to the compressor, leading to an increase in manufacturing cost.

  In addition, if the spring constant is low, the amount of movement of the compressor due to transportation vibration may increase, and the piping connected to the compressor may be deformed or damaged. To eliminate this, the compressor must be within a certain range. It is necessary to add a mechanism that does not displace as described above, which complicates the support mechanism and increases costs.

  There is also a method of suppressing vibration by increasing the thickness of the support frame including the flat portion. However, even if the plate thickness is increased, although the appearance density of the natural frequency gradually decreases, it is difficult to design the cross-sectional structure while avoiding the oscillation frequency of the screw compressor and the second and third harmonics. The effect of the plate thickness is that the vibration is suppressed by the increase in mass due to the increase in the plate thickness. If the plate thickness is about three times empirically, the vibration response can be reduced by about 10 dB. It is. However, when the frame is actually configured with a plate thickness of 10 mm or more, there is a drawback that the weight of the entire apparatus becomes heavy, leading to an increase in material and processing cost.

  By adding simple reinforcement to a frame having a simple cross-sectional structure, the present invention simultaneously achieves suppression of compressor vibration, suppression of pipe vibration originating from compressor vibration, and suppression of frame vibration in a balanced manner. The object of the present invention is to realize an inexpensive heat pump apparatus that greatly reduces the noise of the entire apparatus, has good workability in manufacturing the apparatus, and is inexpensive.

A heat pump device according to the present invention includes a compressor having a refrigerant pipe and a compressor foot, and a frame that is mounted on the compressor and fastened via a fastening mechanism and fixed to an installation surface. In the heat pump device
The underframe has an upper horizontal flange to which a fastening portion of the compressor foot is fastened and a lower horizontal flange to be fixed to the installation surface, and the beam having a cross-sectional shape of a U shape and having an opening is rectangular. Formed,
A reinforcing plate joined to the upper horizontal flange and the lower horizontal flange of the underframe is provided directly under the compressor ,
The length of the joint between the reinforcing plate and the underframe is set to be not less than 1/2 times the resonance wavelength closest to the oscillation frequency of the compressor in the underframe when the reinforcing plate is not joined. it is obtained by the following.

  According to the heat pump device of the present invention, since the reinforcing plate is attached to the lower part of the compressor of the underframe that supports the compressor, it becomes difficult for the flat portion of the underframe to be displaced in the vibration direction. The resonance of the frame with respect to the oscillation frequency is suppressed.

Embodiment 1 FIG.
FIG. 1 is a front view showing a first embodiment of a heat pump device according to the present invention, FIG. 2 is a side view showing the first embodiment of the heat pump device according to the present invention, and FIG. It is an expanded sectional view of the attaching part to attach, and a compressor is a screw compressor which has a gate rotor and a screw rotor at least, or a screw compressor which has a male and female rotor at least.

  The compressor 2 of the heat pump device according to the present invention includes a compressor body 2b to which a discharge side refrigerant pipe 6a and a suction side refrigerant pipe 6b are connected, and a compressor foot 2a for fixing the compressor body 2b to the frame 1. In general, the compressor foot 2a is provided at three or more places, and has upper and lower flat portions 2aa and 2ab parallel to the horizontal flanges 1a and 1b of the frame 1. 1 and 2 show an example in which four compressor legs 2a are provided. An anti-vibration rubber 3a is installed between the flat portion 2ab of the compressor foot 2a and the horizontal flange 1a of the base frame 1 so that the oscillation vibration of the compressor 2 is not directly transmitted to the base frame 1. Anti-vibration rubber 3b is installed between the bolt 4a and the flat portion 2aa. Further, in order to fix the flat portions 2aa, 2ab of the compressor foot 2a and the base frame 1, the bolt 4a is connected to the horizontal flange of the base frame 1, the flat portions 2aa, 2ab of the compressor foot 2a, the vibration isolating rubber 3a, and The anti-vibration rubber 3b is penetrated and fixed by bolts 4a and nuts 4b. Further, a reinforcing plate 5 is provided between the horizontal flanges 1a and 1b immediately below the compressor 2 and joined to the horizontal flanges 1a and 1b by welding.

  In the first embodiment, the underframe 1 is formed of a rectangular U-shaped beam having horizontal flanges 1 a and 1 b and having openings in the horizontal direction, and the horizontal flange 1 a directly below the compressor 2. 1b is provided with a reinforcing plate 5 welded to the horizontal flanges 1a and 1b by welding, so that the resonance of the compressor support frame with respect to the oscillation frequency of the compressor is suppressed and the device is manufactured as will be described later. The above workability is good and an inexpensive heat pump apparatus is realized.

  The compressor 2 used in the heat pump apparatus of the first embodiment is shown as an example of a screw system, and generally there are many things having a weight of 100 kg to 1000 kg. In the specific example of the first embodiment, A screw compressor 2 having a weight of about 400 kg, a width of about 450 mm, a depth of about 1000 mm, and a height of 500 mm is installed. The oscillation frequency was 290 Hz or 360 Hz. The flat surface portion 2ab of the compressor foot 2a has four fixing surfaces having a width of about 100 mm and a depth of about 100 mm.

  A total of four anti-vibration rubbers 3a are installed between the flat portion 2ab of the compressor foot 2a and the horizontal flange 1a of the underframe 1 respectively. Even if the anti-vibration rubber 3a is not provided, there is an effect of suppressing the resonance. However, by providing the anti-vibration rubber 3a, the effect of the anti-vibration rubber 3a is combined and becomes more remarkable than the effect of suppressing the resonance.

  If the anti-vibration rubber 3a is too soft, the amount of movement of the compressor 2 due to transportation vibration increases, and there is a risk that the pipe connected to the compressor 2 may be deformed or damaged. Although it is necessary to add a mechanism that does not displace beyond a certain range, in general, the support mechanism becomes complicated, leading to an increase in cost. In addition, if the vibration isolating rubber 3a is too hard, the vibration of the compressor 2 cannot be prevented from vibration. Therefore, it is desirable to set the dynamic spring constant in the range of 1000 to 10000 N / mm as the total of the four vibration isolating rubbers.

  Further, in order to realize a vibration isolating rubber of 1000 N / mm or less that can support the weight of the compressor 2, it is necessary to increase the thickness of the rubber while maintaining the same width W and depth. Since the degree of freedom in the direction becomes large, it is necessary to form the shape of the mount type anti-vibration rubber.

  In a specific example of the first embodiment, a chloroprene rubber having a thickness of about 10 mm and a rubber hardness of 60 degrees is cut to have the same width W and depth as the flat portion 2ab of the compressor foot 2a. A total of four pieces were placed on each flat surface portion 2ab of the foot 2a. The dynamic spring constant of the anti-vibration rubber at this time was about 7000 N / mm as a total of four.

  The anti-vibration rubber 3b is for preventing the vibration of the compressor foot 2a from being directly transmitted to the bolt 4a, and has a width and depth larger than the flange portion of the bolt 4a, and needs a thickness of several millimeters to 20 mm. is there. In a specific example of the first embodiment, a device having a width of 30 mm, a depth of 30 mm, and a thickness of 5 mm was installed.

  The bolt 4a and the nut 4b are for fastening the compressor 2 to the frame 1, and the main purpose is to maintain the positional relationship between the compressor 2 and the frame against vibrations when the heat pump device is transported. It is. As shown in FIG. 1, the bolt 4a may be inserted from above, or conversely from the frame 1 side, and the upper side may be the nut 4b, and the fixing effect between the compressor 2 and the frame remains unchanged. . In a specific example of the first embodiment, four sets of M16 bolts 4a and nuts 4b are used as a fixed portion of each compressor foot 2a.

  The refrigerant pipe 6 is generally a copper pipe or a steel pipe. In a specific example of the first embodiment, copper pipes having a diameter of about 50 mm and a thickness of about 2 mm were used for the refrigerant pipes 6a and 6b.

  4 to 7 are cross-sectional views showing a general structure of the underframe. FIG. 4 is a underframe 1 employed in the first embodiment, and the underframe 1 is shown in FIGS. Although the frame 17 having a cross-sectional structure as shown in FIG. 4 may be used, the frame 1 having the cross-sectional structure shown in FIG.

  As shown in FIG. 7, in the case of the frame 17 having a completely tubular cross section, the bending rigidity of the beam is excellent, but it is difficult to fasten and fix the bolt and nut for fixing the compressor. In addition, machining such as making a large hole into which the ratchet tool can be inserted at the bottom is necessary, and there is a problem that the machining cost and the material cost increase when used as the underframe 17.

  In the case of the cross-sectional structure as shown in FIG. 6, the bending rigidity in the vertical direction, that is, the load direction of the compressor is strong, but there is an opening at the bottom, so that the opening at the side as shown in FIG. There is a problem that the workability of tightening bolts and nuts is poorer than when there is. Also, for example, if you want to weld a nut, perform the work such as reversing the whole frame 17, making a hole in the side of the nut fixing position, floating the frame from the floor, or disassembling the frame There is a need to.

  The cross-sectional shape having an opening on the side as shown in FIG. 5 and having a lip has almost the same workability as the cross-sectional shape shown in FIG. As a result, the movable range of the welding torch is limited, so that welding workability is poor. Also, when painting, there is a drawback that it is difficult to paint the inner surface. Furthermore, since the bending process is more twice than the cross-sectional shape of FIG. 4, the processing cost is also increased.

  As shown in Fig. 4, when the side of one side is completely open, bolts and nuts can be easily tightened and the nuts can be welded from the side. It's easy to do. Further, when the steel plate material is bent, there is an advantage that the number of times of bending is two and the processing cost is lower than other cross-sectional shapes.

  4 has horizontal flanges at the top and bottom, the upper horizontal flange serves to install and fix the compressor, and the lower horizontal flange makes contact with the ground or the concrete foundation surface when installing the heat pump device. It is easy to fix stably, and it is easy to install anchor bolts because the side faces are open.

  In the first embodiment, the frame 1 having the cross-sectional shape shown in FIG. As a cross-sectional shape in a specific example, in order to place the compressor 2 having a weight of about 400 kg, a steel plate material having a thickness of 4.5 mm was bent to a cross-sectional shape having a width of 75 mm and a height of 150 mm.

  The reinforcing plate 5 is manufactured by cutting a steel plate material in the same manner as the frame 1 and is installed by welding from the side opening portion side of the frame 1 to the upper and lower horizontal flanges of the frame 1.

  The structural requirements of the reinforcing plate 5 are as follows. First, the joining length between the reinforcing plate 5 and the upper and lower horizontal flanges 1a and 1b is determined by the oscillation of the compressor 2 without the reinforcing plate 5 of FIG. The frame 1 needs to be at least one-half of the longest wavelength at which the frame 1 resonates, and preferably has a length of one wavelength or more. In a specific embodiment, the width is 325 mm (resonance wavelength length). . This is because, when the joining length of the reinforcing plate 5 is less than half of the resonance wavelength, the reinforcing plate 5 swings in synchronization with the vertical vibrations of the horizontal flanges 1a and 1b in FIG. . In addition, when the joining length of the reinforcing plate 5 is more than one-half to one wavelength, the reinforcing plate 5 in FIG. 1 may swing in synchronization with the rotation direction, and the vibration reduction effect may be reduced. Therefore, the length is desirably one wavelength or longer. If the joining length of the reinforcing plate 5 has a width of one wavelength or more, the motion of the reinforcing plate 5 cannot be synchronized in the vertical direction or the rotational direction with respect to the resonance wavelength, and the vibration of the horizontal flanges 1a and 1b. Can be effectively suppressed. In addition, if the length of the reinforcing plate 5 is too long, the welding length becomes longer, the processing cost increases, and the material cost of the reinforcing plate 5 increases, so that at most twice the resonance wavelength of the underframe 1 or the compressor foot. The length is preferably between 2a.

  Second, since it is effective to suppress the oscillation of the oscillation source, it is desirable to install a reinforcing plate immediately below the compressor 2, and in the first embodiment, as shown in FIG. Under the compressor 2, and as shown in FIG. 2, it is installed about 1/4 of the protruding length of the horizontal flanges 1a and 1b.

  Third, it is desirable that the natural frequency of the reinforcing plate 5 itself is higher than the oscillation frequency of the compressor 2. In the specific example of the first embodiment, the plate thickness is set to 6 mm and the lowest natural characteristic of the reinforcing plate 5 is used. The frequency f1,1 is about 800 Hz. If the natural frequency of the reinforcing plate 5 is low, the rigidity becomes weak and the effect of suppressing resonance vibration is reduced.

  In the first embodiment, the nut 4b for fastening can be easily fixed to the frame 1 by welding. After the nut 4b is welded, the mounting position of the horizontal portion 2ab of the compressor foot 2a is set to the nut 4b. The bolts 4a can be inserted to fit the compressor 2 and the compressor 2 can be easily fastened to the frame 1. Thereafter, the inner surface of the underframe 1 can be easily painted. After the inner surface coating, the reinforcing plate 5 is joined to the horizontal flanges 1a and 1b of the frame by welding, and then the outer surface coating is performed, whereby all the manufacturing operations can be easily performed.

  As described above, as shown in FIG. 4, the frame 1 having a U-shaped cross-sectional shape having an opening on the side surface is used as a support mechanism for the compressor 2, and the frame 1 is directly below the compressor 2. By providing the reinforcing plate 5, resonance is suppressed, and further, by providing the anti-vibration rubber 3 a, the effects of the anti-vibration rubber 3 a are combined, the resonance suppression effect becomes more remarkable, and noise is reduced.

  Further, by installing a vibration-proof rubber having a dynamic spring constant of 1000 to 10000 N / mm between the compressor foot and the base frame, the effect of suppressing the resonance of the base 1 frame due to the vibration of the compressor 2 becomes more prominent. In addition, the vibration of the compressor 2 itself is moderately suppressed, the vibration of the refrigerant pipe connected to the compressor 2 is moderately suppressed, the vibration of the entire apparatus is suppressed, and the noise emitted from the entire apparatus is reduced. .

Example 1.
To summarize the specific examples in the first embodiment,
・ Compressor: Screw compressor of about 400 kg, transmission frequency of 290 Hz or 360 Hz, width of about 450 mm, depth of about 1000 mm, and height of 500 mm. Rubber: about 7000 N / mm as the total of 4
・ Reinforcement plate: None,
Yes, the plate pressure is 6 mm, the natural frequency f1,1 is 800H, and the joining length is 325 mm.
The result of noise measurement in this configuration is 69 dBA when there is a reinforcing plate and 76 dBA when there is no reinforcing plate, and it was found that the noise reduction effect is large.

Example 2
Table 1 shows the results of noise measurement in a specific Example 2, and Table 2 shows the cost increase in Example 2.

  In the second embodiment, the compressor, the base frame, and the reinforcing plate are the same as those in the first embodiment, and the total of the dynamic spring constants for the four vibration-proof rubbers is 500, 1000, 7000, 10,000, 15000 (N / mm).

From the results shown in Table 1, when the reinforcing plate is installed, the noise is reduced compared to the case where the reinforcing plate is not installed, and the noise value is lowered by providing the anti-vibration rubber. If the dynamic spring constant of the anti-vibration rubber is 10000 N / mm or less, the noise value is suppressed to 70 dBA or less. Further, if the dynamic spring constant is set to 500 N / mm or less, noise may be reduced to 70 dBA or less even without a reinforcing plate. In order to achieve both vibration isolation and stable fixing of the compressor, it is necessary to cope with the mount type vibration isolation rubber, and the cost increases rapidly. If the dynamic spring constant is 1000 N / mm or more, the plate-shaped anti-vibration rubber can be used by cutting it into the size of the flat portion of the compressor foot. Can be kept low.
As described above, by setting the dynamic spring constant to 1000 N / mm or more and 10000 N / mm or less, it is possible to suppress an increase in cost and reduce noise.

  In the first embodiment, an example in which the vibration isolating rubber is used has been shown. However, a spring may be used instead of the vibration isolating rubber. In this case, the dynamic spring constant of the spring is in the range of 1000 to 10000 N / mm. Thus, the same effect can be obtained.

  INDUSTRIAL APPLICABILITY The present invention can be effectively used to reduce vibration and noise of a heat pump device (including a refrigerator) in which a compressor is installed on a frame.

It is a front view which shows Embodiment 1 of the heat pump apparatus which concerns on this invention. It is a side view which shows Embodiment 1 of the heat pump apparatus which concerns on this invention. It is an expanded sectional view of the attaching part which attaches a compressor to a frame. It is an external view which shows the whole heat pump apparatus or the whole structure of a refrigerator. It is sectional drawing which shows the general structure of a frame. It is sectional drawing which shows the general structure of a frame. It is sectional drawing which shows the general structure of a frame.

Explanation of symbols

1 underframe, 1a, 1b horizontal flange, 2 compressor, 2a compressor foot,
2aa, 2ab horizontal part, 3a, 3b anti-vibration rubber, 4a bolt, 4b nut,
5 Reinforcement plate, 6a Discharge side refrigerant piping, 6b Suction side refrigerant piping, 6 Refrigerant piping,
11 Upper plane part of underframe.

Claims (4)

In a heat pump device comprising a compressor having a refrigerant pipe and a compressor foot, and a base frame fixed to the installation surface while the compressor is mounted and fastened via a fastening mechanism portion,
The underframe has an upper horizontal flange to which a fastening portion of the compressor foot is fastened and a lower horizontal flange to be fixed to the installation surface, and the beam having a cross-sectional shape of a U shape and having an opening is rectangular. Formed,
A reinforcing plate joined to the upper horizontal flange and the lower horizontal flange of the underframe is provided directly under the compressor ,
The length of the joint between the reinforcing plate and the underframe is set to be not less than 1/2 times the resonance wavelength closest to the oscillation frequency of the compressor in the underframe when the reinforcing plate is not joined. A heat pump device characterized by the following . 2. The heat pump device according to claim 1 , wherein the natural frequency of the reinforcing plate itself is higher than the oscillation frequency of the compressor . The heat pump device according to claim 1 or 2 , wherein a vibration-proof rubber or a ridge is provided between a fastening portion of the compressor foot and the underframe . 4. The heat pump device according to claim 3, wherein a dynamic spring constant in the vertical direction of the anti-vibration rubber or ridge is set to 1000 to 10,000 N / mm .

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