WO2024166737A1

WO2024166737A1 - Compressor

Info

Publication number: WO2024166737A1
Application number: PCT/JP2024/002772
Authority: WO
Inventors: 諒秋本; 健史上田; 直人多田; 雄大森田
Original assignee: 株式会社富士通ゼネラル
Priority date: 2023-02-10
Filing date: 2024-01-30
Publication date: 2024-08-15
Also published as: JP2024113954A

Abstract

A compressor according to an embodiment of the present invention comprises a compressor housing for accommodating a compression unit whereby a refrigerant is compressed, an accumulator housing connected with an intake section of the compression unit, and a holder member connecting the compressor housing and the accumulator housing. The holder member includes: a housing-facing section having a first surface that is formed along the outer peripheral surface of the compressor housing and is in contact with the outer peripheral surface; an arm section that bends from along the outer peripheral surface toward the accumulator housing side, is formed so as to extend from the housing-facing section, is in contact with the accumulator housing, and supports the accumulator housing; and a joint section whereby the holder member and the compressor housing are joined. At least part of a second surface that is a side surface in the arm section on the compressor housing side in the location at which said arm section bends from along the outer peripheral surface toward the accumulator housing side is included in the joint section.

Description

Compressor

An embodiment of the present invention relates to a compressor.

Conventionally, a hermetic compressor used in air conditioners and freezers is known, which is provided with a refrigerant discharge section and a refrigerant suction section, a compressor housing that houses a compression section that compresses the refrigerant sucked in from the suction section, a motor that drives the compression section, and an accumulator connected to the suction section. In this hermetic compressor, there is a conventional technique in which the accumulator container is fixed to the compressor housing by a holder fixed to the outer circumferential surface of the compressor housing.

JP 2016-61209 A

However, the above conventional technology cannot sufficiently reduce the effects of resonance in the accumulator caused by vibrations in the compressor housing that occur when the compression section is driven, resulting in a problem of large vibrations in the accumulator.

For example, in the above-mentioned Patent Document 1, the contact surface between the holder and the compressor housing is provided circumferentially outward of the welded portion of the holder, thereby increasing the bending rigidity and reducing the amplitude during resonance. However, even if the contact surface with the compressor housing is provided circumferentially outward of the welded portion of the holder, the resonance frequency of the accumulator caused by vibration of the compressor housing is actually considered to be determined by the length of the beam when the welded portion where the compressor housing and the holder are welded is regarded as the fixed portion of the cantilever beam.

In other words, even if the contact surface with the compressor housing is provided circumferentially outside the welded part of the holder, when the compressor housing vibrates, the contact surface of the holder will rise up due to the vibration and will not make contact with the compressor housing, resulting in a gap between the contact surface of the holder and the compressor housing.

As a result, the length of the beam that determines the resonant frequency (eigenvalue) of the accumulator due to vibration of the compressor housing is the length of the holder from the welded part with the compressor housing to the contact point with the accumulator. Therefore, even if the contact surface with the compressor housing is provided circumferentially further outward than the welded part of the holder as in Patent Document 1, the beam length that determines the resonant frequency of the accumulator due to vibration of the compressor housing does not change and remains large.

When the beam length, which determines the resonant frequency, is large, the resonant frequency (eigenvalue) of the accumulator caused by the vibration of the compressor housing is low, so vibrations caused by the effects of resonance tend to increase in a frequency range up to twice the operating speed range of the compressor (the range of possible compressor speeds during operation).

The disclosed technology has been developed in consideration of the above, and aims to provide a compressor that can reduce the effects of accumulator resonance caused by vibrations in the compressor housing.

A compressor according to one aspect of the present disclosure includes a compressor housing that houses a compression section that compresses a refrigerant, an accumulator housing that is connected to a suction section of the compression section, and a holder member that connects the compressor housing and the accumulator housing. The holder member has a housing facing portion that is formed along the outer peripheral surface of the compressor housing and has a first surface that abuts against the outer peripheral surface, an arm portion that is bent toward the accumulator housing from a direction along the outer peripheral surface and formed to extend from the housing facing portion and abuts against the accumulator housing to support the accumulator housing, and a joint portion where the holder member and the compressor housing are joined. The joint portion includes at least a portion of the second surface on the compressor housing side at a portion of the arm portion that bends toward the accumulator housing from a direction along the outer peripheral surface.

The disclosed technology can reduce the effects of accumulator resonance.

FIG. 1 is a vertical cross-sectional view illustrating an example of a rotary compressor according to an embodiment. FIG. 2 is an exploded perspective view of a compression unit (excluding a rotary shaft) of the rotary compressor according to the embodiment, as viewed from above. FIG. 3 is a top view illustrating an example of the rotary compressor according to the embodiment. FIG. 4 is a perspective view of the holder member before joining. FIG. 5 is a view of the holder members before joining, as viewed from the contact surface side. FIG. 6 is a cross-sectional view showing the cross-sectional structure of the dotted line portion in FIG. FIG. 7 is an explanatory diagram for explaining the state of projection welding. FIG. 8 is a cross-sectional view showing a cross-sectional structure of a joint between a holder member and a compressor housing according to the embodiment. FIG. 9 is an explanatory diagram for explaining a typical joint portion of the embodiment. FIG. 10 is an explanatory diagram for explaining a typical joint of a comparative example (conventional example). FIG. 11 is a graph comparing accumulator acceleration during operation between the embodiment and the comparative example. FIG. 12 is a graph illustrating the hammering results in the embodiment and the comparative example.

Below, a compressor according to an embodiment will be described with reference to the drawings. Components having the same functions in the embodiments will be given the same reference numerals, and duplicated descriptions will be omitted. Note that the compressor described in the following embodiment is merely an example, and does not limit the embodiment. In addition, the following embodiments may be combined as appropriate within a range that does not cause contradictions.

FIG. 1 is a vertical cross-sectional view showing an example of a rotary compressor according to an embodiment. FIG. 2 is an exploded perspective view of the compression section (excluding the rotating shaft) of the rotary compressor according to an embodiment, viewed from above.

As shown in FIG. 1, the rotary compressor 1 includes a rotary type compression section 12 arranged at the bottom of a sealed vertically-mounted cylindrical compressor housing 10, a motor 11 arranged above the compression section 12 and driving the compression section 12 via a rotary shaft 15, a vertically-mounted cylindrical accumulator 25 (accumulator housing 25a) fixed to the side of the compressor housing 10, and a housing base (mounting leg) 310 fixed to the bottom of the compressor housing 10 and supporting the entire rotary compressor 1. The accumulator 25 (accumulator housing 25a) has an internal space connected to the lower suction chamber 131S of the lower cylinder 121S via the lower suction pipe 104 and the accumulator lower curved pipe 31S. Similarly, the accumulator 25 (accumulator housing 25a) has an internal space connected to the upper suction chamber 131T of the upper cylinder 121T via the upper suction pipe 105 and the accumulator upper curved pipe 31T. Multiple elastic support members 330 are attached to the housing base (mounting legs) 310.

In addition, a discharge pipe (discharge section) 107 is provided at the center of the top of the compressor housing 10 to pass through the compressor housing 10 and discharge the refrigerant into the refrigerant circuit (refrigeration cycle) of the air conditioner, and an accumulator inlet pipe 255 is provided at the center of the top of the accumulator 25 to pass through the accumulator housing 25a of the accumulator 25 and draw the refrigerant from the suction side piping 256 of the refrigerant circuit (refrigeration cycle) of the air conditioner.

The motor 11 has a stator 111 on the outside and a rotor 112 on the inside, with the stator 111 fixed to the inner surface of the compressor housing 10 by shrink fitting, and the rotor 112 fixed to the rotating shaft 15 of the compression section 12 by shrink fitting.

The rotating shaft 15 is rotatably supported with respect to the entire rotary type compression section 12 by the main shaft section 153 above the upper eccentric section 152T being rotatably supported by the main bearing section 161T provided on the upper end plate 160T, the sub-shaft section 151 below the lower eccentric section 152S being rotatably supported by the sub-bearing section 161S provided on the lower end plate 160S, and the lower eccentric section 152S and the upper eccentric section 152T being rotatably supported by the lower piston 125S and the upper piston 125T, respectively, and the lower piston 125S and the upper piston 125T are caused to revolve by the rotation.

As shown in FIG. 2, the compression section 12 is constructed by stacking, from the top, an upper end plate cover 170T, an upper end plate 160T, an upper cylinder 121T, an intermediate partition plate 140, a lower cylinder 121S, a lower end plate 160S, and a lower end plate cover 170S, and the entire compression section 12 is fixed from above and below by a plurality of through

bolts

174, 175 and auxiliary bolts 176 arranged in a substantially concentric manner.

The lower cylinder 121S has a lower suction hole 135S that fits with the lower suction pipe 104. The upper cylinder 121T has an upper suction hole 135T that fits with the upper suction pipe 105. A lower piston 125S is disposed in the lower cylinder chamber 130S of the lower cylinder 121S. An upper piston 125T is disposed in the upper cylinder chamber 130T of the upper cylinder 121T.

The lower cylinder 121S is provided with a lower vane groove 128S that extends radially outward from the lower cylinder chamber 130S, and a lower vane 127S is disposed in the lower vane groove 128S. The upper cylinder 121T is provided with an upper vane groove 128T that extends radially outward from the upper cylinder chamber 130T, and an upper vane 127T is disposed in the upper vane groove 128T.

A lower spring hole 124S is provided on the outer surface of the lower cylinder 121S at a position overlapping with the lower vane groove 128S in the circumferential direction, with the hole having a depth that does not penetrate into the lower cylinder chamber 130S, and a lower spring 126S is disposed in the lower spring hole 124S. An upper spring hole 124T is provided on the outer surface of the upper cylinder 121T at a position overlapping with the upper vane groove 128T in the circumferential direction, with the hole having a depth that does not penetrate into the upper cylinder chamber 130T, and an upper spring 126T is disposed in the upper spring hole 124T.

The lower cylinder chamber 130S is closed from above and below by the intermediate partition plate 140 and the lower end plate 160S. The upper cylinder chamber 130T is closed from above and below by the upper end plate 160T and the intermediate partition plate 140.

The lower cylinder chamber 130S is divided into a lower suction chamber 131S communicating with the lower suction hole 135S and a lower compression chamber 133S communicating with the lower discharge hole 190S provided in the lower end plate 160S by pressing the lower vane 127S against the outer wall of the lower piston 125S by the lower spring 126S. The upper cylinder chamber 130T is divided into an upper suction chamber 131T communicating with the upper suction hole 135T and an upper compression chamber 133T communicating with the upper discharge hole 190T provided in the upper end plate 160T by pressing the upper vane 127T against the outer wall of the upper piston 125T by the upper spring 126T.

A lower end plate cover chamber 180S is formed between the lower end plate 160S and the lower end plate cover 170S on the outlet side of the lower discharge hole 190S. The lower end plate cover chamber 180S has a recess (not shown) in the lower end plate 161S, which houses a lower discharge valve 200S that prevents refrigerant from flowing back through the lower discharge hole 190S into the lower compression chamber 133S, and a lower discharge valve holder 201S that regulates the opening degree of the lower discharge valve 200S. The lower end plate 160S and the lower end plate cover 170S are fixed tightly to each other.

On the outlet side of the upper discharge hole 190T, an upper end plate cover chamber 180T is formed between the upper end plate 160T and the upper end plate cover 170T, and the upper end plate cover chamber 180T has a recess 181T in the upper end plate 161T, and the recess 181T houses an upper discharge valve 200T that prevents refrigerant from flowing back through the upper discharge hole 190T into the upper compression chamber 133T, and an upper discharge valve holder 201T that regulates the opening degree of the upper discharge valve 200T. The upper end plate 160T and the upper end plate cover 170T are fixed tightly to each other.

Next, the flow of refrigerant caused by the rotation of the rotating shaft 15 will be explained. In the lower cylinder chamber 130S, the rotation of the rotating shaft 15 causes the lower piston 125S fitted to the lower eccentric portion 152S of the rotating shaft 15 to revolve along the inner wall of the lower cylinder chamber 130S, causing the lower suction chamber 131S to expand in volume and draw in refrigerant from the lower suction pipe 104 via the accumulator 25. Similarly, in the upper cylinder chamber 130T, the rotation of the rotating shaft 15 causes the upper piston 125T fitted to the upper eccentric portion 152T of the rotating shaft 15 to revolve along the inner wall of the upper cylinder chamber 130T, causing the upper suction chamber 131T to expand in volume and draw in refrigerant from the upper suction pipe 105 via the accumulator 25.

In addition, the lower compression chamber 133S compresses the refrigerant while reducing its volume, and when the pressure of the compressed refrigerant becomes higher than the pressure in the lower end plate cover chamber 180S outside the lower discharge valve 200S, the lower discharge valve 200S opens and the refrigerant is discharged from the lower compression chamber 133S to the lower end plate cover chamber 180S. Similarly, the upper compression chamber 133T compresses the refrigerant while reducing its volume, and when the pressure of the compressed refrigerant becomes higher than the pressure in the upper end plate cover chamber 180T outside the upper discharge valve 200T, the upper discharge valve 200T opens and the refrigerant is discharged from the upper compression chamber 133T to the upper end plate cover chamber 180T.

The refrigerant discharged into the lower end plate cover chamber 180S passes through the refrigerant passage hole 136 (see FIG. 1) and the upper end plate cover chamber 180T, and is discharged from the upper end plate cover discharge hole 172T (see FIG. 1) into the inside of the compressor housing 10. The refrigerant discharged into the upper end plate cover chamber 180T is discharged from the upper end plate cover discharge hole 172T into the inside of the compressor housing 10.

The refrigerant discharged into the compressor housing 10 is guided above the motor 11 through a notch (not shown) formed on the outer periphery of the stator 111 over the entire vertical direction of the stator 111, or through a gap in the winding part of the stator 111 (not shown), or through a gap between the stator 111 and the rotor 112, and is discharged from the discharge pipe 107 at the top of the compressor housing 10 to the discharge side piping 108.

Figure 3 is a top view showing an example of a rotary compressor according to an embodiment. As shown in Figure 3, the compressor housing 10 that houses the compression section 12 and the accumulator housing 25a are both cylindrical. The cylindrical compressor housing 10 and the accumulator housing 25a are connected via a holder member 30 joined to the compressor housing outer peripheral surface 10a by a welding joint 40, a fastener 35 wrapped around the outer peripheral surface of the accumulator housing 25, and a bolt 34 that engages the holder member 30 and the fastener 35.

The holder member 30 is formed, for example, from metal, and has a housing facing portion 31 and an arm portion 32. The housing facing portion 31 is formed along the compressor housing outer peripheral surface 10a, which is the outer peripheral surface of the compressor housing 10, and abuts against this compressor housing outer peripheral surface 10a. The arm portion 32 is formed so as to continue from each of both ends of the housing facing portion 31, and extends in a direction away from the compressor housing 10. The arm portion 32 has a first folded portion 33a and a second folded portion 33b. The first folded portion 33a is formed so as to continue from the housing facing portion 31, and is formed so as to bend from the direction along the compressor housing outer peripheral surface 10a towards the accumulator housing 25a, and extend toward the abutment portion 32b of the arm portion 32 with the accumulator housing 25a. The second folded portion 33b is formed so as to be continuous with the first folded portion 33a, and is formed so as to extend from the abutment portion 32b of the arm portion 32 with the accumulator housing 25a in a direction away from the accumulator housing 25a.

The holder member 30 has a side surface (third surface) of the arm 32 facing the accumulator housing 25a abutting against the outer peripheral surface of the accumulator housing 25a. As shown in Figs. 3 to 5, the second folded portion 33b of one of the two arms 32 extending from both ends of the holder member 30 has a notch or hole for engaging one end of the fastener 35, for example. The second folded portion 33b of the other of the two arms 32 extending from both ends of the holder member has a bolt hole for fastening the other end of the fastener 35 with a bolt 34, for example. The holder member 30 and the fastener 35, which are connected to each other, hold the accumulator housing 25a between them, thereby fixing the accumulator housing 25a to the compressor housing 10.

The fastener 35 is formed, for example, from a thin metal plate, and is wrapped around the outer peripheral surface of the accumulator housing 25a, as shown in FIG. 3. As described above, one end of the fastener 35 is engaged with the holder member 30, for example, by being hooked onto a notch or hole formed in the arm 32 extending from one end of the housing facing portion 31. The other end of the fastener 35 is fastened to the holder member 30, for example, by a bolt 34 passed through a bolt hole formed in the arm 32 extending from the other end of the housing facing portion 31.

Figure 4 is a perspective view of the holder member 30 before joining. As shown in Figure 4, the housing facing portion 31 has an arc-shaped abutment surface 31a (first surface) that abuts against the compressor housing outer peripheral surface 10a of the cylindrical compressor housing 10. The abutment surface 31a is formed in an arc shape that follows the compressor housing outer peripheral surface 10a, that is, in a convex shape toward the accumulator housing 25a side when viewed from the compressor housing 10. The housing facing portion 31 also has an inner surface 31b (third surface) on the accumulator housing 25a side, which is the side opposite to the abutment surface 31a. A dowel 41 (protrusion) is formed on the abutment surface 31a by pressing from the inner surface 31b side.

Figure 5 shows the holder member 30 before joining, as viewed from the contact surface 31a side. As shown in Figure 5, the dowels 41 are formed on the contact surface 31a of the housing facing portion 31 at a position where the holder member 30 bends from the direction along the compressor housing outer peripheral surface 10a to the accumulator housing 25a side (the rear side of the drawing). Specifically, the dowels 41 are formed in multiples (two in the illustrated example) lined up in the axial direction of the compressor housing 10 (the vertical direction of the drawing) at positions that are boundaries between the contact portions 31 on both the left and right sides of Figure 5 and the first fold portion 33a (positions that overlap with inflection point Q1, described below).

6 is a cross-sectional view of the dotted line portion of FIG. 5 taken along the line A-A, in other words, a cross-sectional view of the cross-sectional structure of the dotted line portion of FIG. 5 taken along the arrow. As shown in FIG. 6, the inflection point Q1 indicates the point where the bending of the side surface of the holder member 30 on the compressor housing 10 side from the direction along the compressor housing outer peripheral surface 10a to the accumulator housing 25a side begins. The bending surface 32a (second surface) is a surface that continues to the abutment surface 31a (first surface) at the inflection point Q1 on the side surface of the holder member 30 on the compressor housing 10 side, and is the side surface on the compressor housing 10 side at the portion (first folded portion 33a) that bends to the accumulator housing 25a side. For example, as shown in FIG. 3 and FIG. 6, the bending surface 32a (second surface) is formed in a convex shape toward the radially outer side of the cylindrical accumulator housing 25a when viewed from the accumulator housing 25a.

The dowel 41 is formed to include at least a portion of the bent surface 32a (second surface). In this embodiment, the dowel 41 is formed to straddle both the abutment surface 31a (first surface) that is formed in a convex shape toward the accumulator housing 25a side when viewed from the compressor housing 10, including the inflection point Q1, and the bent surface 32a (second surface) that is formed in a convex shape toward the radially outer side of the cylindrical accumulator housing 25a when viewed from the accumulator housing 25a.

The holder member 30 is formed, for example, by bending a flat plate-like member by press processing to form the housing-facing portion 31, the first folded portion 33a, and the second folded portion 33b. When forming the holder member 30 described above, for example, while the holder member 30 is in a flat plate-like state, the dowel 41 is first formed by press processing or the like, and then the holder member 30 is bent by press processing, so that the dowel 41 (protrusion) of the holder member 30 can be positioned close to the inflection point Q1, which is the boundary between the abutment surface 31a (first surface) of the housing-facing portion 31 and the folded surface 32a (second surface) of the arm portion 32 (first folded portion 33a).

The holder member 30 is joined to the compressor housing 10 by bringing the contact surface 31a into contact with the compressor housing outer peripheral surface 10a of the compressor housing 10 and then performing projection welding. Figure 7 is an explanatory diagram that diagrammatically explains the projection welding process.

As shown in FIG. 7, in projection welding, the contact surface 31a is brought into contact with the compressor housing outer peripheral surface 10a, and then the projection welding electrode 50 is pressed against the holder member 30 from the inner surface 31b. At this time, the dowel 41 formed on the contact surface 31a of the holder member 30 comes into contact with the compressor housing outer peripheral surface 10a. Next, in projection welding, a large voltage is applied to the projection welding electrode 50, so that a large current flows intensively through the dowel 41 that is in contact with the compressor housing outer peripheral surface 10a, and the heat generated by electrical resistance melts the dowel 41, forming a joint 40 and joining the holder member 30 to the compressor housing 10.

FIG. 8 is a cross-sectional view showing the cross-sectional structure of the joint 40 between the holder member 30 and the compressor housing 10 of the embodiment. FIG. 9 is an explanatory diagram that illustrates the joint 40. As shown in FIGS. 8 and 9, the holder member 30 and the compressor housing 10 are joined by the above-mentioned projection welding at the joint 40 formed at the position where the dowel 41 (protrusion) of the holder member 30 was located, i.e., at a location including at least a part of the bending surface 32a (in this embodiment, a position spanning the abutment surface 31a (first surface) and the bending surface 32a (second surface)).

As shown in FIG. 8, the recess 42 is a recess recessed toward the compressor housing 10, formed by pressing from the inner surface 31b when forming the dowel 41 by press working or the like. The recess 42 is formed across the side surface on the inner surface 31b side corresponding to the dowel 41 (i.e., the side surface behind the abutment surface 31a) and the side surface behind the bent surface 32a.

Figure 10 is a schematic diagram illustrating a joint in a comparative example (conventional). As shown in Figure 10, the joint 400 between the conventional holder member 300 and the compressor housing 10 is located entirely on the compressor housing outer circumferential surface 10a (in other words, the entire joint 400 is located circumferentially further inward than the inflection point Q1, which is the boundary between the abutment surface (first surface) of the housing facing portion and the bent surface (second surface) of the arm portion (first folded portion)), so the beam length that determines the resonant frequency described above remains large.

In contrast, in this embodiment, as shown in FIG. 9, the joint 40 between the holder member 30 and the compressor housing 10 is located so as to include at least a part of the bent surface 32a, which is the side surface of the bent portion (first folded portion 33a) of the arm portion 32 facing the compressor housing 10, and is located further outward in the circumferential direction of the compressor housing outer peripheral surface 10a than in the past. Therefore, in this embodiment, the beam length that determines the above-mentioned resonance frequency is shortened, and the resonance frequency (eigenvalue) of the accumulator 25 connected to the holder member 30 due to the vibration of the compressor housing 10 can be made higher. Therefore, in this embodiment, the resonance frequency shifts to the higher frequency side with respect to the frequency range up to about twice the operating rotation speed of the rotary compressor 1 (the vibration frequency of the compression section 12), so that the effect of resonance within that frequency range is reduced, and the vibration of the accumulator 25 due to the vibration of the compressor housing 10 can be reduced.

FIG. 11 is a graph comparing the measurement results of the circumferential acceleration around the compressor housing 10 (accumulator acceleration) that occurs in the accumulator 25 during operation between the embodiment and the comparative example. The horizontal axis in FIG. 11 is the compressor rotation speed [rps], and the vertical axis is the acceleration [m/s2] in the circumferential direction of the compressor housing 10 that occurs in the accumulator. Graph G1 is a graph illustrating the measurement results during operation of the rotary compressor 1 according to the embodiment. Graph G2 is a graph illustrating the measurement results during operation of a conventional rotary compressor. As shown in FIG. 11, in comparison with graph G2 showing the comparative example, graph G1 showing the embodiment is able to greatly reduce the accumulator acceleration in the compressor rotation speed range of 60 to 140 [rps], where the acceleration [m/s2] value was particularly large in the comparative example.

FIG. 12 is a graph illustrating the results of a hammering test comparing the embodiment and the comparative example. The horizontal axis in FIG. 12 is the frequency of vibration during a hammering test (a test in which an object is vibrated by striking it with a hammer and the acceleration generated in the object as a result of the vibration is measured to examine the frequency response characteristics of the object), and the vertical axis is the frequency response function (FRF) [dB/m/s2/N]. Graph G3 is a graph illustrating the results of a hammering test of the rotary compressor 1 according to the embodiment. Graph G4 is a graph illustrating the results of a hammering test of a comparative example (conventional) rotary compressor. As shown in FIG. 12, in the graph G4 showing the comparative example, the structural eigenvalue (resonance frequency) exists near 300 [Hz] (there is a peak in the frequency response function), whereas in the graph G3 showing the embodiment, the structural eigenvalue (resonance frequency) moves (shifts) to the high frequency side (near 330 [Hz] in the embodiment). That is, in this embodiment, the resonance frequency can be made higher (the eigenvalue can be made larger) compared to the comparative example (conventional example). Therefore, in the graph G3 showing this embodiment, in a frequency range up to twice the operating rotation speed under normal operating conditions of the rotary compressor 1 (for example, when the compressor rotation speed under normal operating conditions of the rotary compressor 1 is in the range of 0 to 140 [rps], the frequency range of twice the rotation speed is 0 to 280 [Hz]), the FRF near 280 [Hz] where the value of the frequency response function is particularly large is smaller by about 10 [dB/m/s2/N] compared to the graph G4 showing the comparative example. That is, vibration due to the influence of resonance is particularly improved on the high frequency side (near 280 [Hz]) in the frequency range twice the operating rotation speed of the rotary compressor 1, which is close to the above-mentioned structural eigenvalue (330 [Hz]). As a result, as shown in FIG. 11, in the rotary compressor 1 of this embodiment, the acceleration caused by the resonance in the accumulator housing 25a is smaller than in the comparative example, and the effect of resonance in the accumulator housing 25a connected to the holder member 30 due to the vibration of the compressor housing 10 is reduced, and the vibration of the accumulator housing 25a can be suppressed.

(Effects of the Compressor of the Embodiment)
As described above, the rotary compressor 1 of the present embodiment includes the compressor housing 10 that houses the compression section 12 that compresses the refrigerant, the accumulator housing 25a that is connected to the suction section of the compression section 12, and the holder member 30 that connects the compressor housing 10 and the accumulator housing 25a. The holder member 30 has a housing facing portion 31, an arm portion 32, and a joint portion 40. The housing facing portion 31 is formed along the compressor housing outer peripheral surface 10a that is the outer peripheral surface of the compressor housing 10. The housing facing portion 31 has an abutment surface 31a (first surface) that abuts against the compressor housing outer peripheral surface 10a. The arm portion 32 is formed so as to bend toward the accumulator housing 25a from the direction along the compressor housing outer peripheral surface 10a and extend from the housing facing portion 31, abut against the accumulator housing 25a, and support the accumulator housing 25a. The joint portion 40 is a portion where the holder member 30 and the compressor housing 10 are joined. When the side surface of the arm portion 32 on the compressor housing 10 side at a portion (first folded portion 33a) that is bent from a direction along the compressor housing outer peripheral surface 10a toward the accumulator housing 25a is defined as a bent surface 32a (second surface), the joint portion 40 includes at least a portion of the bent surface 32a (second surface).

Therefore, the joint 40 between the holder member 30 and the compressor housing 10 is positioned so as to include at least a part of the bent surface 32a (second surface), which is the side surface of the bent portion (first folded portion 33a) of the arm portion 32 on the compressor housing 10 side, so that the welded portion 40 can be positioned further outward in the circumferential direction of the compressor housing outer peripheral surface 10a than in the past. Therefore, in this embodiment, the beam length that determines the above-mentioned resonance frequency is shortened, and the resonance frequency (eigenvalue) of the accumulator 25 (accumulator housing 25a) associated with the vibration of the compressor housing 10 can be made higher. Therefore, the resonance frequency (eigenvalue) shifts to the higher frequency side with respect to a frequency range up to, for example, about twice the operating rotation speed of the rotary compressor 1. As a result, in the embodiment, the acceleration generated in the accumulator housing 25a due to the effect of resonance of the accumulator housing 25a associated with the vibration of the compressor housing 10 is smaller than in the comparative example. As a result, the effect of resonance of the accumulator housing 25a connected to the holder member 30 due to vibration of the compressor housing 10 is reduced, and vibration of the accumulator 25 (accumulator housing 25a) within the frequency range corresponding to the operating speed of the rotary compressor 1 can be suppressed.

More specifically, it is preferable that the joint 40 is provided at a position that satisfies the following conditions on a horizontal plane that passes through the joint 40, as shown in FIG.
The point on the arm portion 32 that abuts against the accumulator housing 25a and is closest to the compressor housing 10 is defined as point P1.
A point on the curved surface 32a that is located more inward than point P1 in the radial direction of the compressor casing 10 and is also located outermost in the circumferential direction of the compressor casing 10 is defined as point P2.
The center of the compressor housing 10 is defined as point O.
・Let the line starting from point O and passing through point P1 be a half line L1.
・Let the line starting from point O and passing through point P2 be a half line L2.
At least a portion of the joint 40 is located between the half line L1 and the half line L2 in the circumferential direction around the compressor casing 10.

By positioning and positional relationship of the joints 40 in this way, the arm 32 can be positioned as far outward as possible in the circumferential direction, and the length of the beam (the part of the arm 32 related to the resonant frequency) mentioned above can be shortened. In addition, the circumferential spacing of the joints 40 is widened, making the fixation stronger and bringing the joints 40 closer to the arm 32. This makes it possible to increase the resonant frequency (eigenvalue) mentioned above.

Furthermore, it is particularly preferable that the position satisfies the following conditions:
A tangent line that starts at point O and touches the outer circumferential surface of the accumulator housing 25a is defined as a half line L3.
The half line L3 is located between the half lines L1 and L2 in the circumferential direction around the compressor casing 10.

REFERENCE SIGNS LIST 1: rotary compressor 10: compressor housing 10a: compressor housing outer peripheral surface 11: motor 12: compression section 15: rotating shaft 25: accumulator 25a: accumulator housing 30: holder member 31: housing facing portion 31a: contact surface (first surface)
31b...Inner surface (third surface)
31S... accumulator lower curved tube 31T... accumulator upper curved tube 32... arm portion 32a... curved surface (second surface)
32b...Abutment portion 33...Folded portion 33a...First folded portion 33b...Second folded portion 34...Bolt 35...Fastener 40...Joint portion 41...Dowel 42...Recess 50...Projection welding electrode 104...Lower suction pipe 105...Upper suction pipe 107...Discharge pipe 111...Stator 112...Rotor 121S...Lower cylinder 121T...Upper cylinder 124S...Lower spring hole 124T...Upper spring hole 125S...Lower piston 125T...Upper piston 126S...Lower spring 126T...Upper spring 127S...Lower vane 127T...Upper vane 128S...Lower vane groove 128T...Upper vane groove 130S...Lower cylinder chamber 130T...Upper cylinder chamber 131S...Lower suction chamber 131T...Upper suction chamber 133S...Lower compression chamber 133T...Upper compression chamber 135 S...Lower suction hole 135T...Upper suction hole 136...Refrigerant passage hole 140...Middle partition plate 151...Subshaft part 152S...Lower eccentric part 152T...Upper eccentric part 153...Main shaft part 160S...Lower end plate 160T...Upper end plate 161S...Sub bearing part 161T...Main bearing part 170S...Lower end plate cover 170T...Upper end plate cover 172T...Upper end plate Cover discharge hole 174...Through bolt 175... Through bolt 176... auxiliary bolt 180S... lower end plate cover chamber 180T... upper end plate cover chamber 181T... recess 190S... lower discharge hole 190T... upper discharge hole 200S... lower discharge valve 200T... upper discharge valve 201S... lower discharge valve holder 201T... upper discharge valve holder 255... accumulator inlet pipe 300... holder member 400... joint portion 310... housing base (mounting leg)
330...Elastic support members G1 to G4...Graphs L1 to L3...Semi-lines O, P1, P2...Point Q1...Inflection point

Claims

a compressor housing that houses a compression unit that compresses a refrigerant;
an accumulator housing connected to a suction portion of the compression portion;
a holder member that connects the compressor housing and the accumulator housing,
The holder member includes:
a housing facing portion that is formed along an outer circumferential surface of the compressor housing and has a first surface that abuts against the outer circumferential surface;
an arm portion that is bent from a direction along the outer circumferential surface toward the accumulator housing and is formed to extend from the housing facing portion and abut against the accumulator housing to support the accumulator housing;
a joint portion at which the holder member and the compressor housing are joined,
The joint portion includes at least a part of a second surface that is a side surface of the compressor housing at a portion of the arm portion that is bent from a direction along the outer circumferential surface toward the accumulator housing.
A compressor characterized by:
The joint portion is formed so as to span the first surface and the second surface.
2. The compressor according to claim 1 .
The compressor housing and the accumulator housing are cylindrical,
The first surface is formed in a convex shape toward the accumulator housing side when viewed from the compressor housing,
The second surface is formed in a convex shape toward an outer side in a radial direction of the accumulator housing when viewed from the accumulator housing.
2. The compressor according to claim 1 .
The joint portion is provided in a plurality of parts in the axial direction of the compressor housing.
4. The compressor according to claim 3.
A recess is formed in a third surface of the holder member on the accumulator side, the recess being recessed toward the compressor housing.
2. The compressor according to claim 1 .
The recess is formed on the third surface across a side surface on the rear side of the first surface and a side surface on the rear side of the second surface.
6. The compressor according to claim 5.
In a horizontal plane passing through the joint,
a first point is a point of the arm portion that is in contact with the accumulator housing and closest to the compressor housing;
a second point is a point on the second surface that is located inside the first point in a radial direction of the compressor casing and is located outermost in a circumferential direction of the compressor casing;
a line starting from the center of the compressor housing and passing through the first point is defined as a first ray;
When a line that starts at the center of the compressor housing and passes through the second point is defined as a second ray,
At least a portion of the joint is located between the first half line and the second half line in the circumferential direction of the compressor housing.
2. The compressor according to claim 1 .
In a horizontal plane passing through the joint,
When a tangent line that starts from the center of the compressor housing and touches the outer peripheral surface of the accumulator housing is defined as a third half line,
The third half line is located between the first half line and the second half line in the circumferential direction of the compressor housing.
8. The compressor according to claim 7.