Patent Description:
Conventionally, as in Patent Literature <NUM> (<CIT>), a compressor is known in which a welding pin is press-fitted into a hole formed on an outer surface of a support that supports a bearing, and the welding pin and a casing are welded to fix the support to the casing. A compressor is also known from <CIT>, that comprises the technical features of the preamble of the independent claim.

In such a compressor, when the welding pin is press-fitted into the support, the welding pin is plastically deformed. Also, when the welding pin and the casing are welded, the welding pin is pressed against the support by thermal expansion of the welding pin, and the welding pin is further plastically deformed. When the welding pin is excessively plastically deformed, a holding force of the welding pin after welding may decrease.

Aim of the present invention is to provide a compressor and a refrigeration cycle apparatus which improve the state of the art indicated above. This aim is achieved by the compressor according to independent claim <NUM>, the dependent claims defining preferred embodiments of the invention.

An embodiment of a compressor will be described below with reference to the drawings.

An outline of a scroll compressor <NUM> as an embodiment of a compressor of the present disclosure will be described with reference to <FIG> is a schematic longitudinal cross-sectional view of the scroll compressor <NUM>.

The scroll compressor <NUM> is used in a refrigeration cycle apparatus <NUM> using a vapor compression refrigeration cycle such as an air conditioner, a hot water supply apparatus, and a floor heating device. For example, the scroll compressor <NUM> is mounted in a heat source unit of the refrigeration cycle apparatus <NUM>, and constitutes a part of a refrigerant circuit of the refrigeration cycle apparatus <NUM>.

The refrigeration cycle apparatus <NUM> includes, for example, a refrigerant circuit <NUM> as illustrated in <FIG>. The refrigerant circuit <NUM> mainly includes the scroll compressor <NUM>, a condenser (radiator) <NUM>, an expansion device <NUM>, and an evaporator <NUM>. In the refrigerant circuit <NUM>, the scroll compressor <NUM>, the condenser <NUM>, the expansion device <NUM>, and the evaporator <NUM> are connected by pipes as illustrated in <FIG>. The condenser <NUM> and the evaporator <NUM> are heat exchangers. For example, the expansion device <NUM> may be an electric expansion valve whose opening degree is variable or a capillary tube.

As an optional configuration, in the present embodiment, the refrigerant circuit <NUM> includes a subcooling heat exchanger <NUM> and a bypass expansion device <NUM>. The subcooling heat exchanger <NUM> is a heat exchanger in which a refrigerant flowing through a bypass pipe <NUM> and a refrigerant flowing through the refrigerant circuit <NUM> from the condenser <NUM> to the expansion device <NUM> exchange heat. The bypass pipe <NUM> is a pipe connecting a branch portion <NUM>, on a pipe connecting the condenser <NUM> and the expansion device <NUM> in the refrigerant circuit <NUM>, and a below-mentioned injection pipe 18c of the scroll compressor <NUM>. The bypass expansion device <NUM> is, for example, an electric expansion valve whose opening degree is variable. The refrigerant flowing through the refrigerant circuit <NUM> from the condenser <NUM> to the expansion device <NUM> is cooled by heat exchange performed in the subcooling heat exchanger <NUM>, becomes a refrigerant in a subcooled state, and flows to the expansion device <NUM>. The refrigerant that has flowed through the bypass pipe <NUM>, has been decompressed to an intermediate pressure in a refrigeration cycle (pressure between high and low pressure in the refrigeration cycle, hereinbelow sometimes simply referred to as an intermediate pressure) in the bypass expansion device <NUM>, and has been subjected to heat exchange with the refrigerant flowing through the subcooling heat exchanger <NUM> from the condenser <NUM> to the expansion device <NUM> is injected into a below-mentioned compression mechanism <NUM> of the scroll compressor <NUM>.

In the refrigerant circuit <NUM>, the scroll compressor <NUM> sucks a gas refrigerant having a low pressure in the refrigeration cycle (hereinbelow sometimes simply referred to as a low pressure) and compresses the gas refrigerant in the compression mechanism <NUM>. The gas refrigerant having a high pressure in the refrigeration cycle (hereinbelow sometimes simply referred to as a high pressure) compressed in the compression mechanism <NUM> and discharged from the scroll compressor <NUM> radiates heat and condenses in the condenser <NUM> to become a high-pressure liquid refrigerant. The refrigerant condensed in the condenser <NUM> flows to the expansion device <NUM>. Part of the refrigerant flowing from the condenser <NUM> toward the expansion device <NUM> flows through the bypass pipe <NUM>, is decompressed to the intermediate pressure by the bypass expansion device <NUM>, cools the refrigerant flowing toward the expansion device <NUM> in the subcooling heat exchanger <NUM>, and is then injected into the compression mechanism <NUM> of the compressor <NUM>. The refrigerant that has passed through the subcooling heat exchanger <NUM> and flowed to the expansion device <NUM> is decompressed in the expansion device <NUM> and becomes a gas-liquid two-phase refrigerant having a low pressure in the refrigeration cycle (hereinbelow sometimes simply referred to as a low pressure). The low-pressure gas-liquid two-phase refrigerant, having flowed through the subcooling heat exchanger <NUM> and decompressed in the expansion device <NUM>, absorbs heat in the evaporator <NUM> and evaporates to become a low-pressure gas refrigerant. The low-pressure gas refrigerant that has exited the evaporator <NUM> is sucked into the scroll compressor <NUM> again and compressed.

For example, in a case where the refrigeration cycle apparatus <NUM> is an air conditioner, during cooling operation, a heat exchanger mounted on a utilization unit functions as the evaporator <NUM> and a heat exchanger mounted on a heat source unit functions as the condenser <NUM>. Whereas, during heating operation, the heat exchanger mounted on the utilization unit functions as the condenser <NUM> and the heat exchanger mounted on the heat source unit functions as the evaporator <NUM>. In a case where the refrigeration cycle apparatus <NUM> is an air conditioner and the air conditioner is used for both cooling and heating, the refrigeration cycle apparatus <NUM> further includes a flow path switching mechanism (not illustrated) such as a four-way switching valve to be used to switch between cooling operation and heating operation.

The scroll compressor <NUM> of the present disclosure is a fully hermetic compressor. As described above, the scroll compressor <NUM> sucks the low-pressure refrigerant, compresses the sucked refrigerant into a high-pressure refrigerant in the refrigeration cycle, and discharges the high-pressure refrigerant. The refrigerant is, for example, an HFC refrigerant R32. Note that R32 is merely an example of the refrigerant, and the scroll compressor <NUM> may be a device that compresses one or more HFC refrigerant other than R32 or one or more HFO refrigerant. Also, for example, the scroll compressor <NUM> may be a device that compresses and discharges a natural refrigerant such as carbon dioxide.

As illustrated in <FIG>, the scroll compressor <NUM> mainly includes a casing <NUM>, the compression mechanism <NUM>, a housing <NUM>, a welding pin <NUM>, a motor <NUM>, a drive shaft <NUM>, and a lower bearing housing <NUM>.

Details of the casing <NUM>, the compression mechanism <NUM>, the housing <NUM>, the welding pin <NUM>, the motor <NUM>, the drive shaft <NUM>, and the lower bearing housing <NUM> will be described.

The scroll compressor <NUM> includes the casing <NUM> having a longitudinally elongated cylindrical shape (refer to <FIG>).

The casing <NUM> mainly includes a cylindrical member <NUM>, an upper lid 14a, and a lower lid 14b. The cylindrical member <NUM> is a cylindrical member extending along a center axis O and opened on upper and lower sides. The upper lid 14a is provided on an upper side of the cylindrical member <NUM> and closes an upper opening of the cylindrical member <NUM>. The lower lid 14b is provided on the lower side of the cylindrical member <NUM> and closes a lower opening of the cylindrical member <NUM>. The cylindrical member <NUM>, the upper lid 14a, and the lower lid 14b are fixed by welding to maintain a hermetic state.

The casing <NUM> houses therein various members constituting the scroll compressor <NUM> including the compression mechanism <NUM>, the housing <NUM>, the motor <NUM>, the drive shaft <NUM>, and the lower bearing housing <NUM> (refer to <FIG>). The compression mechanism <NUM> is disposed in an upper part of the casing <NUM>. The housing <NUM> is disposed below the compression mechanism <NUM>. The motor <NUM> is disposed below the housing <NUM>. The lower bearing housing <NUM> is disposed below the motor <NUM>. An oil reservoir space <NUM> is formed in a bottom part of the casing <NUM>. Refrigerator oil for lubricating various sliding portions of the scroll compressor <NUM> is stored in the oil reservoir space <NUM>.

The motor <NUM> is disposed in a first space S1 of the scroll compressor <NUM>. In the scroll compressor <NUM> of the present embodiment, the first space S1 is a space into which a high-pressure refrigerant compressed by the compression mechanism <NUM> flows. In other words, the scroll compressor <NUM> of the present embodiment is a so-called high-pressure dome-type scroll compressor. The first space S1 communicates with the oil reservoir space <NUM> in a lower part of the casing <NUM> via a gap or the like formed between the cylindrical member <NUM> of the casing <NUM> and a below-mentioned stator <NUM> of the motor <NUM> (refer to <FIG>).

Note that the scroll compressor <NUM> does not need to be is a high-pressure dome-type scroll compressor. For example, the compressor of the present disclosure may be a so-called low-pressure dome-type scroll compressor in which a motor is disposed in a space into which a low-pressure refrigerant flows from the refrigerant circuit <NUM> of the refrigeration cycle apparatus <NUM>.

A suction pipe 18a, a discharge pipe 18b, and the injection pipe 18c are attached to the casing <NUM> so that an inside of the casing <NUM> communicate with an outside of the casing <NUM> via these pipes (refer to <FIG>).

As illustrated in <FIG>, the suction pipe 18a is provided to penetrate the upper lid 14a of the casing <NUM>. One end (an end portion outside the casing <NUM>) of the suction pipe 18a is connected to a pipe extending from the evaporator <NUM> of the refrigerant circuit <NUM> of the refrigeration cycle apparatus <NUM>, and the other end (an end portion inside the casing <NUM>) of the suction pipe 18a is connected to a suction port 36a of a fixed scroll <NUM> of the compression mechanism <NUM>. The suction pipe 18a communicates with a below-mentioned compression chamber Sc on an outer peripheral side of the compression mechanism <NUM> via the suction port 36a. The scroll compressor <NUM> sucks a low-pressure refrigerant in the refrigeration cycle of the refrigeration cycle apparatus <NUM> via the suction pipe 18a.

As illustrated in <FIG>, the discharge pipe 18b is provided at a center of the cylindrical member <NUM> in an up-down direction so as to penetrate the cylindrical member <NUM>. One end (an end portion outside the casing <NUM>) of the discharge pipe 18b is connected to a pipe extending to the condenser <NUM> of the refrigerant circuit <NUM> of the refrigeration cycle apparatus <NUM>, and the other end (an end portion inside the casing <NUM>) of the discharge pipe 18b is disposed between the housing <NUM> and the motor <NUM> in the first space S1. The scroll compressor <NUM> discharges a high-pressure refrigerant compressed by the compression mechanism <NUM> via the discharge pipe 18b.

As illustrated in <FIG>, the injection pipe 18c is provided to penetrate the upper lid 14a of the casing <NUM>. One end (an end portion outside the casing <NUM>) of the injection pipe 18c is connected to the bypass pipe <NUM> of the refrigerant circuit <NUM> of the refrigeration cycle apparatus <NUM>, and the other end (an end portion inside the casing <NUM>) of the injection pipe 18c is connected to the fixed scroll <NUM> of the compression mechanism <NUM>. The injection pipe 18c communicates with the compression chamber Sc being in a midstream of compression in the compression mechanism <NUM> via a not-illustrated passage formed in the fixed scroll <NUM>. The compression chamber Sc, with which the injection pipe 18c communicates and which is in the midstream of compression, is supplied with an intermediate-pressure refrigerant in the refrigeration cycle from the refrigerant circuit <NUM> of the refrigeration cycle apparatus <NUM> via the injection pipe 18c.

The compression mechanism <NUM> mainly includes the fixed scroll <NUM> and a movable scroll <NUM>. The fixed scroll <NUM> and the movable scroll <NUM> are combined to form the compression chamber Sc. The compression mechanism <NUM> compresses a refrigerant in the compression chamber Sc and discharges the compressed refrigerant.

The fixed scroll <NUM> is mounted on and fastened to the housing <NUM> with a not-illustrated fixing means (for example, a bolt).

As illustrated in <FIG>, the fixed scroll <NUM> mainly includes a fixed-side end plate <NUM>, a fixed-side wrap <NUM>, and a peripheral edge portion <NUM>.

The fixed-side end plate <NUM> is a circular plate-shaped member. The fixed-side wrap <NUM> is a wall-shaped member protruding toward the movable scroll <NUM> from a front surface 32a (lower surface) of the fixed-side end plate <NUM>. When the fixed scroll <NUM> is seen from below, the fixed-side wrap <NUM> is formed in a spiral shape (an involute shape) from a region near a center toward an outer periphery of the fixed-side end plate <NUM>. The peripheral edge portion <NUM> is a thick cylindrical member protruding from the front surface 32a of the fixed-side end plate <NUM> toward the movable scroll <NUM>. The peripheral edge portion <NUM> is disposed to surround the periphery of the fixed-side wrap <NUM>. The peripheral edge portion <NUM> is provided with the suction port 36a. A downstream end of the suction pipe 18a is connected to the suction port 36a.

The fixed-side wrap <NUM> of the fixed scroll <NUM> and a movable-side wrap <NUM> of the movable scroll <NUM> are combined to form the compression chamber Sc. Specifically, the fixed scroll <NUM> and the movable scroll <NUM> are combined in a state where the front surface 32a of the fixed-side end plate <NUM> and a front surface 42a (upper surface) of a movable-side end plate <NUM> are opposed to each other. As a result, the compression chamber Sc surrounded by the fixed-side end plate <NUM>, the fixed-side wrap <NUM>, the movable-side wrap <NUM>, and the below-mentioned movable-side end plate <NUM> of the movable scroll <NUM> is formed (refer to <FIG>). When the movable scroll <NUM> turns with respect to the fixed scroll <NUM>, a low-pressure refrigerant flowing from the suction pipe 18a via the suction port 36a into the peripheral edge-side compression chamber Sc is compressed. The pressure of the refrigerant increases as the refrigerant approaches the center-side compression chamber Sc.

The fixed-side end plate <NUM> has at its approximately center part a discharge port <NUM> through which the refrigerant compressed by the compression mechanism <NUM> is discharged. The discharge port <NUM> is formed to penetrate the fixed-side end plate <NUM> in a thickness direction (up-down direction) (refer to <FIG>). The discharge port <NUM> communicates with the center-side (innermost-side) compression chamber Sc in the compression mechanism <NUM>. A discharge valve <NUM> that opens and closes the discharge port <NUM> is attached to an upper side of the fixed-side end plate <NUM>. When a pressure in the innermost-side compression chamber Sc, with which the discharge port <NUM> communicates, is equal to or higher than a pressure in a discharge space Sa above the discharge valve <NUM> by a predetermined value, the discharge valve <NUM> is opened to cause the refrigerant in the innermost-side compression chamber Sc to pass through the discharge port <NUM> and flow into the discharge space Sa above the fixed-side end plate <NUM>. The discharge space Sa communicates with a not-illustrated refrigerant passage formed over the fixed scroll <NUM> and the housing <NUM>. The refrigerant passage is a passage that causes the discharge space Sa and the first space S1 below the housing <NUM> to communicate with each other. The refrigerant compressed by the compression mechanism <NUM> and then flowing into the discharge space Sa passes through the refrigerant passage and flows into the first space S1.

As illustrated in <FIG>, the movable scroll <NUM> mainly includes the movable-side end plate <NUM>, the movable-side wrap <NUM>, and a boss portion <NUM>.

The movable-side end plate <NUM> is a circular plate-shaped member. The movable-side wrap <NUM> is a wall-shaped member protruding toward the fixed scroll <NUM> from the front surface 42a (upper surface) of the movable-side end plate <NUM>. When the movable scroll <NUM> is seen from above, the movable-side wrap <NUM> is formed in a spiral shape (an involute shape) from a region near a center toward an outer periphery of the movable-side end plate <NUM>. The boss portion <NUM> is a cylindrical member protruding from a back surface 42b (lower surface) of the movable-side end plate <NUM> toward the motor <NUM>.

While the scroll compressor <NUM> is operating, the movable scroll <NUM> is pressed against the fixed scroll <NUM> by a pressure of a crank chamber <NUM> and a back pressure space <NUM>, which will be described below, disposed on a side of a back surface 42b of the movable-side end plate <NUM>. Since the movable scroll <NUM> is pressed against the fixed scroll <NUM>, leakage of the refrigerant from a gap between a tip of the fixed-side wrap <NUM> and the movable-side end plate <NUM> and a gap between a tip of the movable-side wrap <NUM> and the fixed-side end plate <NUM> is reduced.

The boss portion <NUM> is disposed in the below-mentioned crank chamber <NUM> formed by the housing <NUM>. The boss portion <NUM> is formed in a cylindrical shape. The boss portion <NUM> extends to protrude downward from the back surface 42b of the movable-side end plate <NUM>. An upper portion of the cylindrical boss portion <NUM> is closed by the movable-side end plate <NUM>. A bearing metal <NUM> is disposed in a hollow part of the boss portion <NUM>. A below-mentioned eccentric portion <NUM> of the drive shaft <NUM> is inserted into the hollow part of the boss portion <NUM> (refer to <FIG>). The drive shaft <NUM> is connected to a rotor <NUM> of the motor <NUM> as described below. Therefore, when the motor <NUM> is operated and the rotor <NUM> rotates, the movable scroll <NUM> turns.

The movable scroll <NUM>, which is turned by the motor <NUM>, does not rotate by itself but moves in orbit with respect to the fixed scroll <NUM> by means of an Oldham coupling <NUM> (refer to <FIG>) disposed on the side of the back surface 42b of the movable scroll <NUM>.

When the movable scroll <NUM> moves in orbit with respect to the fixed scroll <NUM>, the gas refrigerant in the compression chamber Sc of the compression mechanism <NUM> is compressed. More specifically, when the movable scroll <NUM> moves in orbit, the gas refrigerant is sucked from the suction pipe 18a via the suction port 36a into the peripheral edge-side compression chamber Sc, and thereafter, the compression chamber Sc moves toward a center of the compression mechanism <NUM> (center of the fixed-side end plate <NUM>). As the compression chamber Sc moves toward the center of the compression mechanism <NUM>, a volume of the compression chamber Sc decreases and a pressure in the compression chamber Sc increases. As a result, the center-side compression chamber Sc has a higher pressure than the peripheral edge-side compression chamber Sc. The gas refrigerant compressed by the compression mechanism <NUM> to have a high pressure is discharged from the center-side compression chamber Sc through the discharge port <NUM> formed in the fixed-side end plate <NUM> into the discharge space Sa. The refrigerant discharged into the discharge space Sa passes through the not-illustrated refrigerant passage formed through the fixed scroll <NUM> and the housing <NUM>, and flows into the first space S1 below the housing <NUM>.

The housing <NUM> will be described with reference to <FIG> as well.

<FIG> is a perspective view of the housing <NUM> as viewed from below. <FIG> is a schematic side view of the housing <NUM>. <FIG> is a schematic view of a fixed state between the casing <NUM> and the welding pin <NUM>.

The housing <NUM> is a cast product. As illustrated in <FIG>, the housing <NUM> mainly includes a main body portion <NUM> and an upper bearing housing <NUM>. The main body portion <NUM> is a cylindrical part. The upper bearing housing <NUM> also has a cylindrical shape. The upper bearing housing <NUM> is disposed closer to the motor <NUM> than the main body portion <NUM> in an axial direction of the drive shaft <NUM>. The upper bearing housing <NUM> is disposed close to the compression mechanism <NUM> than the motor <NUM>.

The housing <NUM> is an example of a support. The housing <NUM> supports a bearing metal <NUM> provided in the upper bearing housing <NUM>.

The fixed scroll <NUM> is fixed to the main body portion <NUM> of the housing <NUM>. Specifically, the fixed scroll <NUM> is mounted on the housing <NUM> in a state where a lower surface of the peripheral edge portion <NUM> of the fixed scroll <NUM> is opposed to an upper surface of the housing <NUM>, and is fixed to the housing <NUM> by a not-illustrated fixing member (for example, a bolt). The housing <NUM> supports the fixed scroll <NUM> fixed to the main body portion <NUM>.

The housing <NUM> also supports the movable scroll <NUM> disposed between the fixed scroll <NUM> and the main body portion <NUM> of the housing <NUM>. The housing <NUM> supports the movable scroll <NUM> from below via the Oldham coupling <NUM> disposed on an upper side of the housing <NUM>.

The main body portion <NUM> of the housing <NUM> is a cylindrical member. The main body portion <NUM> of the housing <NUM> is fixed to an inner peripheral surface of the cylindrical member <NUM> of the casing <NUM>.

Specifically, the housing <NUM> is press-fitted into the cylindrical member <NUM> of the casing <NUM>, and an outer peripheral surface of the main body portion <NUM> is in close contact with an inner peripheral surface of the cylindrical member <NUM>, partially in the axial direction of the drive shaft <NUM>, in entire circumference.

The housing <NUM> is further fixed to the cylindrical member <NUM> of the casing <NUM> by welding. The fixing of the housing <NUM> to the cylindrical member <NUM> by welding will specifically be described.

As illustrated in <FIG> and <FIG>, holes <NUM> into which the welding pins <NUM> are press-fitted are formed on an outer surface <NUM> (outside surface) of the main body portion <NUM> of the housing <NUM>. Each of the holes <NUM> have a substantially equal shape to a cross section of the welding pin <NUM> obtained by cutting the welding pin <NUM> in a direction orthogonal to a press-fitting direction of the welding pin <NUM> (a direction in which the welding pin <NUM> is press-fitted into the hole <NUM>). In the present embodiment, each of the holes <NUM> has a circular shape. The holes <NUM> do not penetrate the main body portion <NUM> in a radial direction of the cylindrical member <NUM> of the casing <NUM>. In other words, the holes <NUM> are concave portions that do not penetrate the housing <NUM> in the radial direction of the cylindrical member <NUM>.

Although dimensions are not limited, in the present embodiment, a diameter D of the hole <NUM> is <NUM>, and a depth A of a portion having the diameter D is <NUM>. The depth A of the hole <NUM> means a depth of the hole <NUM> from the outer surface <NUM> to a bottom portion <NUM> of the hole <NUM> of the main body portion <NUM> of the housing <NUM>. The bottom portion <NUM> of the hole <NUM> means an inner wall portion of the portion having the diameter D of the hole <NUM> in the radial direction of the cylindrical member <NUM>. Although a number is not limited, the holes <NUM> are formed at a total of eight positions on the outer surface <NUM> of the housing <NUM>. Although a position is not limited, on the outer surface <NUM> of the housing <NUM>, the holes <NUM> are formed at four locations at intervals of <NUM>° in a circumferential direction. At each of four locations, the holes <NUM> are formed at two positions in the axial direction (here, an up-down direction) of the drive shaft <NUM>.

In the present embodiment, the shapes and dimensions of the holes <NUM> are all equal. However, the present invention is not limited thereto, and the shape and dimension of the hole <NUM> may vary depending on the position.

For convenience of description, among the holes <NUM> formed at two positions in the axial direction of the drive shaft <NUM>, a hole disposed on an upper side is labeled with reference sign 124b, and a hole disposed on a lower side is labeled with reference sign 124a. For convenience of description, in some cases, the hole <NUM> disposed on the lower side is referred to as a first hole 124a, and the hole <NUM> disposed on the upper side is referred to as a second hole 124b.

A low rigidity region <NUM> is provided at least a part of a periphery of an adjacent portion <NUM> adjacent to the hole <NUM> of the housing <NUM>. The low rigidity region <NUM> has lower rigidity than the adjacent portion <NUM> and including a thin portion 128a to be described below. The low rigidity region <NUM> will be described below.

A through hole 12a is formed at positions of the cylindrical member <NUM> of the casing <NUM> that correspond to the welding pin <NUM> of the housing <NUM> press-fitted into the cylindrical member <NUM> (a position corresponding to the hole <NUM> of the housing <NUM>) as illustrated in <FIG>. At a position of the through hole 12a, the welding pin <NUM> press-fitted into the hole <NUM> and the cylindrical member <NUM> of the casing <NUM> are welded and fixed. A portion indicated by reference sign <NUM> in <FIG> indicates a welded portion between the welding pin <NUM> and the cylindrical member <NUM>. As a result of the welding pin <NUM> press-fitted into the hole <NUM> of the main body portion <NUM> of the housing <NUM> being welded and fixed to the cylindrical member <NUM>, the housing <NUM> is fixed to the cylindrical member <NUM> of the casing <NUM> by welding as well.

Note that the housing <NUM> and the casing <NUM> are not directly welded, but the welding pin <NUM> and the casing <NUM> are welded. This is because the housing <NUM> is a cast product and it is generally difficult to weld the cast product.

The housing <NUM> will further be described.

As illustrated in <FIG>, the main body portion <NUM> of the housing <NUM> includes a first concave portion <NUM> disposed to be recessed at a center and a second concave portion <NUM> disposed to surround the first concave portion <NUM>. The first concave portion <NUM> constitutes a side surface of the crank chamber <NUM> in which the boss portion <NUM> of the movable scroll <NUM> is disposed. The second concave portion <NUM> forms the annular back pressure space <NUM> on the side of the back surface 42b of the movable-side end plate <NUM>.

During operation of the scroll compressor <NUM>, the refrigerator oil flows into the crank chamber <NUM> from the oil reservoir space <NUM>. Therefore, during steady operation of the scroll compressor <NUM> (in a state where operation of the scroll compressor <NUM> is stable), a pressure of the crank chamber <NUM> becomes a high pressure in the refrigeration cycle of the refrigeration cycle apparatus <NUM>. As a result, during the steady operation of the scroll compressor <NUM>, a center portion of the back surface 42b of the movable-side end plate <NUM> facing the crank chamber <NUM> is pushed toward the fixed scroll <NUM> at the high pressure.

When the movable scroll <NUM> turns during operation of the scroll compressor <NUM>, the back pressure space <NUM> communicates with the compression chamber Sc in the midstream of compression via a not-illustrated hole formed in the movable-side end plate <NUM> for a predetermined period during one turn of the movable scroll <NUM>. Therefore, during the steady operation of the scroll compressor <NUM>, a pressure in the back pressure space <NUM> becomes the intermediate pressure in the refrigeration cycle of the refrigeration cycle apparatus <NUM> (a pressure between the high and low pressure in the refrigeration cycle of the refrigeration cycle apparatus <NUM>). As a result, during the steady operation of the scroll compressor <NUM>, a peripheral edge portion of the back surface 42b of the movable-side end plate <NUM> facing the back pressure space <NUM> is pushed toward the fixed scroll <NUM> at the intermediate pressure.

As a result of the above configuration, during the steady operation of the scroll compressor <NUM>, the movable scroll <NUM> is pressed against the fixed scroll <NUM> by the high pressure in the crank chamber <NUM> and the intermediate pressure in the back pressure space <NUM>. The crank chamber <NUM> and the back pressure space <NUM> are separated from each other by an annular wall portion <NUM> disposed at a boundary between the first concave portion <NUM> and the second concave portion <NUM> (refer to <FIG>). A not-illustrated seal ring is disposed on an upper end of the wall portion <NUM> opposed to the back surface 42b of the movable-side end plate <NUM> so as to seal a space between the crank chamber <NUM> and the back pressure space <NUM>.

The upper bearing housing <NUM> has a cylindrical shape. The bearing metal <NUM> that rotatably supports the drive shaft <NUM> is provided inside the cylindrical upper bearing housing <NUM>. The bearing metal <NUM> is an example of a bearing. During operation of the scroll compressor <NUM>, a moment that causes the drive shaft <NUM> to fall may act on the drive shaft <NUM>. An elastic groove <NUM> is formed in a connection portion between the upper bearing housing <NUM> and the main body portion <NUM> so as to allow inclination of the upper bearing housing <NUM> when the moment acts on the drive shaft <NUM>.

The welding pin <NUM> is a member press-fitted into the hole <NUM> of the main body portion <NUM> of the housing <NUM> and a hole <NUM> of the lower bearing housing <NUM> described below.

The welding pin <NUM> will be described with reference to <FIG> as well. <FIG> is a view of the welding pin <NUM> before being press-fitted into the hole <NUM> of the main body portion <NUM> of the housing <NUM> or the hole <NUM> of the lower bearing housing <NUM> as viewed along the direction orthogonal to the press-fitting direction of the welding pin <NUM>. <FIG> is a view of the welding pin <NUM> before being press-fitted into the hole <NUM> of the main body portion <NUM> of the housing <NUM> or the hole <NUM> of the lower bearing housing <NUM> as viewed along the press-fitting direction of the welding pin <NUM>. The press-fitting direction of the welding pin <NUM> means a direction in which the welding pin <NUM> is press-fitted into the hole <NUM> of the main body portion <NUM> of the housing <NUM> or the hole <NUM> of the lower bearing housing <NUM>.

Here, the welding pin <NUM> will be described by taking the welding pin <NUM> press-fitted into the hole <NUM> of the main body portion <NUM> of the housing <NUM> as an example.

As is apparent from <FIG>, the welding pin <NUM> is a substantially cylindrical member. As illustrated in <FIG>, the welding pin <NUM> has a substantially circular shape when viewed along the press-fitting direction of the welding pin <NUM>.

A concave-convex surface <NUM> having a concave-convex shape is provided on an outer periphery of the welding pin <NUM>. Specifically, a plurality of grooves <NUM> are formed along the press-fitting direction of the welding pin <NUM> on the outer periphery of the welding pin <NUM>. In other words, a flat knurling is formed on at least a part of an outer peripheral surface of the welding pin <NUM> by knurling. As a result of such a configuration, when the welding pin <NUM> is viewed along the press-fitting direction of the welding pin <NUM>, a convex portion 62a and a concave portion 62b (portion of the groove <NUM>) are disposed alternately along a circumferential direction of the welding pin <NUM> on the outer peripheral surface of the welding pin <NUM> (refer to <FIG>).

A dimension of the welding pin <NUM> in a radial direction (direction orthogonal to the press-fitting direction of the welding pin <NUM>), a length L of the welding pin <NUM> (length in the press-fitting direction of the welding pin <NUM>), and a shape of the welding pin <NUM> are appropriately designed so that the welding pin <NUM> can be press-fitted into the hole <NUM>. Although not limited, the length L of the welding pin <NUM> is <NUM>.

The welding pin <NUM> is fixed to the main body portion <NUM> of the housing <NUM> by being press-fitted into the hole <NUM> of the main body portion <NUM> of the housing <NUM>. When press-fitted into the hole <NUM>, the convex portion 62a of the welding pin <NUM> is partially plastically deformed. Further, the welding pin <NUM> is expanded due to heat input at a time of welding with the cylindrical member <NUM> of the casing <NUM>, and the convex portion 62a of the welding pin <NUM> is pressed against an inner surface of the hole <NUM>, so that the convex portion 62a of the welding pin <NUM> is further plastically deformed at the time of welding. Since the welding pin <NUM> thermally expanded during welding contracts after welding, a holding force of the welding pin <NUM> with respect to the main body portion <NUM> of the housing <NUM> may be lower than that before welding because an elasticity of the convex portion 62a is lowered due to plastic deformation. Here, the holding force of the welding pin <NUM> with respect to the main body portion <NUM> of the housing <NUM> means a magnitude of a maximum force with which the welding pin <NUM> does not move in a direction opposite to the press-fitting direction when a force in the direction opposite to the press-fitting direction of the welding pin <NUM> is applied to the welding pin <NUM> press-fitted into the main body portion <NUM>.

When the drive shaft <NUM> rotates, the moment acts on the drive shaft <NUM>, and a moment also acts on the upper bearing housing <NUM> provided with the bearing metal <NUM> pivotally supporting the drive shaft <NUM>. As a result, during operation of the scroll compressor <NUM>, a force may repeatedly act on the main body portion <NUM> of the housing <NUM> at least partially in a direction of being away from the casing <NUM>. In a case where the holding force of the welding pin <NUM> is too small, there is a possibility that the welding pin <NUM> is displaced in the direction opposite to the press-fitting direction due to an influence of the moment, and a problem such as lowering of a fixing force of the housing <NUM> with respect to the cylindrical member <NUM> of the casing <NUM> may occur. To suppress excessive lowering of the holding force of the welding pin <NUM>, at least a part of the periphery of the adjacent portion <NUM> adjacent to the hole <NUM> of the main body portion <NUM> of the housing <NUM> is provided with the low rigidity region <NUM>. The low rigidity region <NUM> has lower rigidity than the adjacent portion <NUM> and includes the thin portion 128a to be described below.

As a measure for raising the holding force of the welding pin <NUM>, it is also conceivable to increase the length L of the welding pin <NUM> in the press-fitting direction. However, it may be difficult to increase the length L of the welding pin <NUM> from viewpoints of avoiding an increase in size of the scroll compressor <NUM> and avoiding contact between welding pin <NUM> and other parts (for example, a fixing member that fixes the housing <NUM> and the fixed scroll <NUM> to each other).

The motor <NUM> is an example of an actuator. The motor <NUM> includes an annular stator <NUM> fixed to an inner wall surface of the cylindrical member <NUM> of the casing <NUM>, and the rotor <NUM> disposed on an inner side of the stator <NUM> (refer to <FIG>).

The rotor <NUM> is rotatably housed on the inner side of the stator <NUM> with a small gap (not illustrated) from the stator <NUM>. The rotor <NUM> is coupled to the movable scroll <NUM> of the compression mechanism <NUM> via the drive shaft <NUM>. Specifically, the rotor <NUM> is coupled to the boss portion <NUM> of the movable scroll <NUM> via the drive shaft <NUM> (refer to <FIG>). The motor <NUM> turns the movable scroll <NUM> by rotating the rotor <NUM>.

The drive shaft <NUM> couples the rotor <NUM> of the motor <NUM> to the movable scroll <NUM> of the compression mechanism <NUM>. The drive shaft <NUM> extends in the up-down direction. The drive shaft <NUM> transmits a driving force of the motor <NUM> to the movable scroll <NUM> of the compression mechanism <NUM>.

The drive shaft <NUM> mainly includes a main shaft <NUM> and the eccentric portion <NUM> (refer to <FIG>).

The main shaft <NUM> extends in the up-down direction from the oil reservoir space <NUM> to the crank chamber <NUM>. The main shaft <NUM> is rotatably supported by the bearing metal <NUM> of the upper bearing housing <NUM> and a bearing metal <NUM> disposed in the lower bearing housing <NUM>. The main shaft <NUM> is inserted into and coupled to the rotor <NUM> of the motor <NUM> at a position between the upper bearing housing <NUM> of the housing <NUM> and the lower bearing housing <NUM>. A center axis of the main shaft <NUM> coincides with the center axis O of the cylindrical member <NUM> of the casing <NUM>.

The eccentric portion <NUM> is disposed at an upper end of the main shaft <NUM>. A center axis of the eccentric portion <NUM> is eccentric to the center axis of the main shaft <NUM>. The eccentric portion <NUM> is inserted into the boss portion <NUM> of the movable scroll <NUM> and is rotatably supported by the bearing metal <NUM> disposed inside the boss portion <NUM>.

The drive shaft <NUM> has an oil passage <NUM>. The oil passage <NUM> includes a main passage 86a and a branch passage (not illustrated). The main passage 86a extends from a lower end to an upper end of the drive shaft <NUM> in the axial direction of the drive shaft <NUM>. The branch passage branches off the main passage and extends in a direction intersecting with the axial direction of the drive shaft <NUM>. The refrigerator oil in the oil reservoir space <NUM> is pumped up by a pump (not illustrated) disposed at the lower end of the drive shaft <NUM>, and is then supplied to, for example, sliding portions between the drive shaft <NUM> and the bearing metals <NUM>, <NUM>, and <NUM>, and a sliding portion of the compression mechanism <NUM>, via the oil passage <NUM>.

The lower bearing housing <NUM> (refer to <FIG>) is disposed below the motor <NUM>.

The lower bearing housing <NUM> mainly includes a main body portion <NUM> and a plurality of arms <NUM> extending from the main body portion <NUM> in the radial direction of the cylindrical member <NUM> of the casing <NUM>. Although a number is not limited, the lower bearing housing <NUM> has three arms <NUM>. The lower bearing housing <NUM> is a cast product.

The main body portion <NUM> is formed in a cylindrical shape. The bearing metal <NUM> that rotatably supports the drive shaft <NUM> is provided inside the cylindrical main body portion <NUM>.

Although a structure is not limited, on the main body portion <NUM>, the three arms <NUM> are provided at substantially equal intervals (at <NUM>° intervals) in a circumferential direction of the cylindrical member <NUM> of the casing <NUM>. On an outer peripheral surface of an end portion of each of the arms <NUM> (a surface, of the end portion of the arm <NUM> extending from the main body portion <NUM>, opposed to the cylindrical member <NUM> of the casing <NUM>), the hole <NUM> into which the welding pin <NUM> is press-fitted is formed.

A shape of the hole <NUM> formed in the arm <NUM> is equal to the hole <NUM> formed in the main body portion <NUM> of the housing <NUM>. However, the shape of the hole <NUM> formed in the arm <NUM> is not limited thereto, and for example, the shape of the hole <NUM> may be different from the hole <NUM> formed in the main body portion <NUM> of the housing <NUM>. Here, a detailed description of the hole <NUM> is omitted in order to avoid duplication of description.

Holes (not illustrated) similar to the through hole 12a illustrated in <FIG> are formed in the cylindrical member <NUM> of the casing <NUM> at a position corresponding to the welding pin <NUM> of the lower bearing housing <NUM> (a position corresponding to the hole <NUM> of the lower bearing housing <NUM>). At the position of the through hole, the welding pin <NUM> and the cylindrical member <NUM> of the casing <NUM> are fixed by welding. As a result of the welding pin <NUM> press-fitted into the hole <NUM> of the lower bearing housing <NUM> being welded and fixed to the cylindrical member <NUM>, the lower bearing housing <NUM> is fixed to the cylindrical member <NUM> of the casing <NUM> by welding.

To suppress excessive lowering of the holding force of the welding pin <NUM>, at least a part of the periphery of the adjacent portion <NUM> adjacent to the hole <NUM> of the main body portion <NUM> of the housing <NUM> is provided with the low rigidity region <NUM>. The low rigidity region <NUM> has lower rigidity than the adjacent portion <NUM> and includes the thin portion 128a to be described below.

The reason why the excessive lowering of the holding force of the welding pin <NUM> is suppressed by providing the low rigidity region <NUM> is generally as follows.

When the welding pin <NUM> press-fitted into the hole <NUM> is welded, the welding pin <NUM> is thermally expanded by heat input. If the low rigidity region <NUM> including the thin portion 128a does not exist, a deformation around the hole <NUM> is relatively strongly restricted. Therefore, a large force acts on the thermally expanded welding pin <NUM> from the main body portion <NUM> of the housing <NUM>, and a plastic deformation of the convex portion 62a of the welding pin <NUM> tends to progress.

On the other hand, in a case where the low rigidity region <NUM> including the thin portion 128a having lower rigidity than the adjacent portion <NUM> exists as shown in the present embodiment, when the welding pin <NUM> is thermally expanded, the adjacent portion <NUM> adjacent to the hole <NUM> is relatively easily deformed in accordance with the thermal expansion of the welding pin <NUM>. Therefore, a force exerted on the welding pin <NUM> by the adjacent portion <NUM> becomes relatively small, and the plastic deformation of the convex portion 62a of the welding pin <NUM> tends to be suppressed. In short, the low rigidity region <NUM> including the thin portion 128a is a deformation allowing region that allows deformation of the housing <NUM> when the welding pin <NUM> is thermally expanded.

In the present embodiment, the low rigidity regions <NUM> are disposed around the first holes 124a out of the holes <NUM> of the main body portion <NUM> of the housing <NUM> provided at two positions in the axial direction of the drive shaft <NUM> at each of four locations in the circumferential direction of the cylindrical member <NUM> of the casing <NUM>. The first hole 124a is a hole disposed closest to the bearing metal <NUM> in the axial direction of the drive shaft <NUM> out of the two holes <NUM> provided in the axial direction of the drive shaft <NUM>.

The low rigidity region <NUM> will be described in detail with reference to <FIG> and <FIG> as well as <FIG>. <FIG> is a schematic partial cross-sectional view taken along line VII-VII in <FIG>. In <FIG>, the welding pin <NUM> is not drawn. <FIG> is a schematic partial longitudinal cross-sectional view for explaining an overlapping state between a region where a downgage <NUM> to be described below exists and a region where the welding pin <NUM> exists.

First, the adjacent portion <NUM> will be described. The adjacent portion <NUM> exists at a position adjacent to the first hole 124a of the main body portion <NUM> of the housing <NUM>. The adjacent portion <NUM> is disposed so as to surround an entire circumference of the first hole 124a when the first hole 124a formed in the outer surface <NUM> of the main body portion <NUM> is viewed from a position just facing the first hole 124a. In the adjacent portion <NUM>, in the radial direction of the cylindrical member <NUM> of the casing <NUM>, a member (cast product constituting the housing <NUM>) exists from the outer surface <NUM> of the main body portion <NUM> of the housing <NUM> to at least a position of the depth A of the first hole 124a. In other words, the adjacent portion <NUM> has a thickness of at least "A" in the radial direction of the cylindrical member <NUM> of the casing <NUM>. In particular, in the present embodiment, in the adjacent portion <NUM>, the member exists in a range from the outer surface <NUM> of the main body portion <NUM> to the crank chamber <NUM> in the radial direction of the cylindrical member <NUM> of the casing <NUM>. In the adjacent portion <NUM>, a member having a thickness of K (refer to <FIG>) at minimum exists in the radial direction of the cylindrical member <NUM> of the casing <NUM>.

The low rigidity region <NUM> having lower rigidity than the adjacent portion <NUM> is provided in at least a part of the periphery of the adjacent portion <NUM>. The low rigidity region <NUM> includes the thin portion 128a having a smaller thickness in the radial direction of the cylindrical member <NUM> of the casing <NUM> than the adjacent portion <NUM>. In addition, the low rigidity region <NUM> includes a void portion 128b in which the main body portion <NUM> (member constituting the main body portion <NUM>) does not exist.

The thin portion 128a is disposed, so as to interpose the first hole 124a, on both sides of the first hole 124a in the circumferential direction of the cylindrical member <NUM> of the casing <NUM> (refer to <FIG> and <FIG>). The thin portion 128a is an example of a first portion. In the thin portion 128a, the downgage <NUM> is formed closer to the center axis O (refer to <FIG>) of the cylindrical member <NUM> of the casing <NUM> than the outer surface <NUM> of the main body portion <NUM> of the housing <NUM>. In other words, in the thin portion 128a, when the main body portion <NUM> of the housing <NUM> is viewed from a side provided with the motor <NUM>, a concave portion <NUM> is formed closer to the center axis O of the cylindrical member <NUM> of the casing <NUM> than the outer surface <NUM> of the main body portion <NUM> of the housing <NUM> (refer to <FIG>). As illustrated in <FIG> and <FIG>, the downgage <NUM> is disposed on both sides of each of the four first holes 124a in the circumferential direction of the cylindrical member <NUM> of the casing <NUM> so as to interpose the first hole 124a. The downgage <NUM>, that is, the concave portion <NUM>, is formed from a bottom portion of the main body portion <NUM> of the housing <NUM> to an intermediate portion between the first hole 124a and the second hole 124b in the axial direction of the drive shaft <NUM> (refer to <FIG> and <FIG>). The downgage <NUM> may be provided during casting or by machining the cast product.

As a result of forming the downgage <NUM>, a thickness M of the thin portion 128a of the casing <NUM> in the radial direction of the cylindrical member <NUM> is smaller than a minimum thickness K of the adjacent portion <NUM>. The thickness M of the thin portion 128a in the radial direction of the cylindrical member <NUM> means a total thickness of a portion where a member exists, disposed between the outer surface <NUM> of the main body portion <NUM> and the crank chamber <NUM> in the circumferential direction of the cylindrical member <NUM>. For example, in <FIG>, a total of a thickness M1 and a thickness M2 is the thickness M of the thin portion 128a in the radial direction of the cylindrical member <NUM>. For example, the thickness M of the thin portion 128a does not need to be uniform as illustrated in <FIG>, or the thin portion 128a may be formed so that the thickness M is uniform.

In the thin portion 128a of the present embodiment, the thickness M1 from the outer surface <NUM> of the main body portion <NUM> to the downgage <NUM> is smaller than the depth A of the first hole 124a in the radial direction of the cylindrical member <NUM> of the casing <NUM>. In short, in the adjacent portion <NUM>, the member exists from the outer surface <NUM> of the main body portion <NUM> to a position of a thickness A (= the depth A of the first hole 124a) in the radial direction of the cylindrical member <NUM> of the casing <NUM>, whereas in the thin portion 128a, the thickness M1 from the outer surface <NUM> of the main body portion <NUM> to the downgage <NUM> is smaller than the thickness A in the radial direction of the cylindrical member <NUM> of the casing <NUM>.

In the radial direction of the cylindrical member <NUM> of the casing <NUM>, the region where the downgage <NUM> exists and the region where the welding pin <NUM> press-fitted into the first hole 124a exists overlap with each other in a range of <NUM>% or more of a length of the welding pin <NUM> press-fitted into the first hole 124a in the radial direction of the cylindrical member <NUM> of the casing <NUM> (in other words, the length L of the welding pin <NUM> in the press-fitting direction). It is assumed that the welding pin <NUM> is press-fitted to a position where the welding pin abuts against the bottom portion <NUM> of the first hole 124a. In other words, in the radial direction of the cylindrical member <NUM> of the casing <NUM>, a value B obtained by subtracting the thickness M1 from the outer surface <NUM> of the main body portion <NUM> to the downgage <NUM> in the thin portion 128a from the depth A of the first hole 124a is preferably <NUM>% or more of the length L of the welding pin <NUM> in the press-fitting direction. More specifically, for example, in the radial direction of the cylindrical member <NUM> of the casing <NUM>, a value obtained by subtracting an average of the thicknesses from the outer surface <NUM> of the main body portion <NUM> to the downgage <NUM> in the thin portion 128a from the depth A of the first hole 124a is preferably <NUM>% or more of the length L of the welding pin <NUM> in the press-fitting direction.

The void portion 128b is disposed closer to the motor <NUM> than the first hole 124a in the axial direction of the drive shaft <NUM>. In other words, the void portion 128b is disposed below the first hole 124a in the axial direction of the drive shaft <NUM>. In short, as illustrated in <FIG>, the main body portion <NUM> (member constituting the main body portion <NUM>) does not exist in at least a partial region below the adjacent portion <NUM> below the first hole 124a. Since the void portion 128b exists, a thickness C of the main body portion <NUM> outside a position of the bottom portion <NUM> of the first hole 124a in the radial direction of the cylindrical member <NUM> of the casing <NUM> at a height position where the void portion 128b exists below the adjacent portion <NUM> below the first hole 124a is smaller than the depth A of the first hole 124a (refer to <FIG>). In <FIG>, a mode in which the main body portion <NUM> exists in a partial region immediately below the adjacent portion <NUM> adjacent below the first hole 124a is illustrated, but the present invention is not limited thereto. The main body portion <NUM> does not need to exist immediately below the adjacent portion <NUM> adjacent below the first hole 124a. In other words, for example, only the void portion 128b may be disposed immediately below the adjacent portion <NUM> adjacent below the first hole 124a.

In the present embodiment, as a result of providing the thin portion 128a and the void portion 128b, as illustrated in <FIG>, the low rigidity region <NUM> is provided in a region (angular region indicated by "α" in <FIG>) at <NUM>° or more around a center of the first hole 124a when the first hole 124a is viewed from a position just facing the first hole 124a (when the first hole 124a is viewed from its front in a horizontal direction orthogonal to the axial direction of the drive shaft <NUM>).

A ratio of a minimum distance d from the first hole 124a to the low rigidity region <NUM> to the diameter D of the first hole 124a is preferably <NUM> or more and <NUM> or less. In the present embodiment, since the diameter D of the first hole 124a is <NUM>, the minimum distance d from the first hole 124a to the low rigidity region <NUM> is preferably <NUM> or more and <NUM> or less. In other words, the downgage <NUM> is preferably disposed to be away from the first hole 124a by <NUM> or more and not to be away from the first hole 124a by more than <NUM>. Also, the void portion 128b is preferably disposed to be away from the first hole 124a by <NUM> or more and not to be away from the first hole 124a by more than <NUM>.

By providing the first hole 124a away from the low rigidity region <NUM> by <NUM> or more, that is, by providing the adjacent portion <NUM> of <NUM> or more around the first hole 124a, it is possible to avoid a problem that a rigidity of the adjacent portion <NUM> is lowered and the welding pin <NUM> cannot firmly be held. In other words, by setting the ratio of the minimum distance d from the first hole 124a to the low rigidity region <NUM> to the diameter D of the first hole 124a to <NUM> or more and providing the adjacent portion <NUM> of <NUM> × D or more around the first hole 124a, it is possible to avoid a problem that the rigidity of the adjacent portion <NUM> is excessively lowered and the welding pin <NUM> cannot be held.

In addition, by not providing the first hole 124a away from the low rigidity region <NUM> by more than <NUM>, that is, by preventing the ratio of the minimum distance d from the first hole 124a to the low rigidity region <NUM> to the diameter D of the first hole 124a from exceeding <NUM>, plastic deformation of the convex portion 62a of the welding pin <NUM> at a time of welding tends to be suppressed.

Although not limited, in the present embodiment, the minimum distance d from the first hole 124a to the low rigidity region <NUM> is designed in a range of <NUM> to <NUM>. In other words, the ratio of the minimum distance d from the first hole 124a to the low rigidity region <NUM> to the diameter D of the first hole 124a is preferably in a range of <NUM> to <NUM>.

In order to verify an effect of providing the thin portion 128a, a comparison experiment of the holding force of the welding pin <NUM> press-fitted into the first hole 124a was conducted between a case where the thin portion 128a is provided in the scroll compressor <NUM> and a case where the thin portion 128a is not provided in the scroll compressor <NUM>. The comparative experiment was performed under an equal condition except whether or not to provide the thin portion 128a (for example, dimensions and materials of the welding pin <NUM> and the main body portion <NUM>, welding conditions, and the like and the like are set to the same in the both experiments). As a result of the experiment, an average value P2 of the holding forces of the welding pins <NUM> press-fitted into the first holes 124a in the case where the thin portion 128a is provided is about <NUM> times an average value P1 of the holding forces of the welding pins <NUM> press-fitted into the first holes 124a in the case where the thin portion 128a is not provided (P2 ≈ <NUM> P1).

Operation of the scroll compressor <NUM> will be described. Here, the operation of the scroll compressor <NUM> in a steady state (a state where the operation is started and reaches a stable state) will be described.

When the motor <NUM> is driven, the rotor <NUM> rotates, and the drive shaft <NUM> coupled to the rotor <NUM> also rotates. When the drive shaft <NUM> rotates, the movable scroll <NUM> does not rotate by itself but moves in orbit with respect to the fixed scroll <NUM> by means of the Oldham coupling <NUM>. The low-pressure refrigerant in the refrigeration cycle of the refrigeration cycle apparatus <NUM> flowing from the suction pipe 18a is sucked into the peripheral edge-side compression chamber Sc of the compression mechanism <NUM> via the suction port 36a. As the volume of the compression chamber Sc decreases along with orbital motion of the movable scroll <NUM>, the pressure in the compression chamber Sc increases. Also, the intermediate-pressure (pressure between high and low pressure) refrigerant in the refrigeration cycle of the refrigeration cycle apparatus <NUM> is injected into the compression chamber Sc in the midstream of compression from the injection pipe 18c as needed. The pressure of the refrigerant increases as the refrigerant approaches the center-side (inner side) compression chamber Sc from the peripheral edge-side (outer side) compression chamber Sc and finally becomes a high pressure in the refrigeration cycle of the refrigeration cycle apparatus <NUM>. The refrigerant compressed by the compression mechanism <NUM> is discharged from the discharge port <NUM> located near a center of the fixed-side end plate <NUM>, passes through the not-illustrated refrigerant passage formed through the fixed scroll <NUM> and the housing <NUM>, and flows into the first space S1. The high-pressure refrigerant in the refrigeration cycle is discharged from the first space S1 through the discharge pipe 18b.

(<NUM>-<NUM>)
The scroll compressor <NUM> of the present embodiment includes the motor <NUM> as an example of a actuator, the compression mechanism <NUM>, the drive shaft <NUM>, the housing <NUM> as an example of a support, the casing <NUM>, and the welding pin <NUM>. The drive shaft <NUM> transmits a driving force of the motor <NUM> to the compression mechanism <NUM>. The housing <NUM> supports the bearing metal <NUM> (a bearing metal <NUM> provided in an upper bearing housing <NUM>) as an example of a bearing that rotatably supports the drive shaft <NUM>. At least one hole <NUM> is formed in the outer surface <NUM> of the main body portion <NUM> of the housing <NUM>. The casing <NUM> accommodates the drive shaft <NUM> and the housing <NUM> therein. The casing <NUM>, in particular, the cylindrical member <NUM>, has a cylindrical shape. The concave-convex surface <NUM> having a concave-convex shape is provided on the outer periphery of the welding pin <NUM>. The welding pin <NUM> is press-fitted into the hole <NUM> of the housing <NUM> and is welded and fixed to the casing <NUM>. At least a part of the periphery of the adjacent portion adjacent to the hole <NUM> of the housing <NUM>, particularly in the present embodiment, at least a part of the periphery of the adjacent portion <NUM> adjacent to a first hole 124a, is provided with the low rigidity region <NUM> having lower rigidity than the adjacent portion <NUM>. The low rigidity region <NUM> includes the thin portion 128a having a smaller thickness in the radial direction of the casing <NUM> than the adjacent portion <NUM>.

In the scroll compressor <NUM> of the present embodiment, the periphery of the adjacent portion <NUM> adjacent to the hole <NUM> of the housing <NUM> into which the welding pin <NUM> is press-fitted is provided with the low rigidity region <NUM> including the thin portion 128a and having lower rigidity than the adjacent portion <NUM>. By providing the low rigidity region <NUM>, the housing <NUM> can deform when the welding pin <NUM> is thermally expanded at a time of welding, and plastic deformation of a convex portion 62a of a concave-convex surface <NUM> of the welding pin <NUM> can be suppressed. As a result of suppressing the plastic deformation of the welding pin <NUM>, a relatively large holding force of the welding pin <NUM> can be maintained after welding.

(<NUM>-<NUM>)
In the low rigidity region <NUM> of the scroll compressor <NUM> of the present embodiment, the downgage <NUM> is formed closer to a center axis O of the casing <NUM> than the outer surface <NUM> of the main body portion <NUM> of the housing <NUM>.

In the scroll compressor <NUM> of the present embodiment, by forming the downgage <NUM> around the adjacent portion <NUM>, it is possible to suppress plastic deformation of the convex portion 62a of the concave-convex surface <NUM> of the welding pin <NUM> when the welding pin <NUM> is thermally expanded.

(<NUM>-<NUM>)
In the scroll compressor <NUM> of the present embodiment, when the hole <NUM> (the first hole 124a in the present embodiment) is viewed from a position just facing the hole <NUM>, the low rigidity region <NUM> is provided in a region at <NUM>° or more around a center of the first hole 124a.

In the scroll compressor <NUM> of the present embodiment, by providing the low rigidity region <NUM> in the region at <NUM>° or more around the center of the first hole 124a, the housing <NUM> can deform when the welding pin <NUM> is thermally expanded and plastic deformation of the convex portion 62a of the concave-convex surface <NUM> of the welding pin <NUM> may be suppressed.

(<NUM>-<NUM>)
In the scroll compressor <NUM> of the present embodiment, the ratio (= d/D) of the minimum distance d from the hole <NUM> (the first hole 124a in the present embodiment) to the low rigidity region <NUM> to the diameter D of the first hole 124a is <NUM> or more and <NUM> or less.

By setting the ratio (= d/D) of the minimum distance d from the first hole 124a to the low rigidity region <NUM> to the diameter D of the first hole 124a to <NUM> or more, the scroll compressor <NUM> of the present embodiment can maintain a strength of the housing <NUM> holding the welding pin <NUM>.

Further, in the scroll compressor <NUM> of the present embodiment, the ratio (= d/D) of the minimum distance d from the first hole 124a to the low rigidity region <NUM> to the diameter D of the first hole 124a is <NUM> or less. In other words, in the scroll compressor <NUM> of the present embodiment, the low rigidity region <NUM> is disposed relatively close to the first hole 124a. As a result, when the welding pin <NUM> is thermally expanded, the housing <NUM> can deform, and plastic deformation of the convex portion 62a of the concave-convex surface <NUM> of the welding pin <NUM> can be suppressed.

(<NUM>-<NUM>)
In the scroll compressor <NUM> of the present embodiment, the plurality of holes <NUM> are disposed in an axial direction of the drive shaft <NUM>. In the present embodiment, the first hole 124a and the second hole 124b are provided in the axial direction of the drive shaft <NUM>. In the present embodiment, the low rigidity region <NUM> having lower rigidity than the adjacent portion <NUM> is provided at least a part of the periphery of the adjacent portion <NUM> (an example of the first adjacent portion) adjacent to the first hole 124a disposed closest to the bearing metal <NUM> in the axial direction of the drive shaft <NUM> among the holes.

In the scroll compressor <NUM> of the present embodiment, the low rigidity region <NUM> is provided at least around the first hole 124a where the welding pin <NUM> may receive a largest force (moment) during operation of the compressor. As a result, it is possible to suppress lowering of the holding force of the welding pin <NUM> press-fitted into the first hole 124a after welding.

(<NUM>-<NUM>)
The compressor of the present embodiment is the scroll compressor <NUM>, and the housing <NUM> supports the bearing (bearing metal <NUM>) disposed closer to the compression mechanism <NUM> than the motor <NUM>.

The scroll compressor <NUM> of the present embodiment can suppress lowering of the holding force of the welding pin <NUM> after welding, which is used for the housing <NUM> of the scroll compressor <NUM> on which a large force tends to act.

(<NUM>-<NUM>)
In the scroll compressor <NUM> of the present embodiment, the low rigidity region <NUM> includes the thin portion 128a as an example of a first portion and the void portion 128b as an example of a second portion. The thin portion 128a is disposed, so as to interpose the first hole 124a, on both sides of the first hole 124a in a circumferential direction of the cylindrical member <NUM> of the casing <NUM>. The void portion 128b is disposed closer to the motor <NUM> than the first hole 124a in the axial direction of the drive shaft <NUM>.

In the scroll compressor <NUM> of the present embodiment, as the low rigidity region <NUM> is disposed so as to surround the first hole 124a on three sides, the housing <NUM> can deform relatively largely when the welding pin <NUM> is thermally expanded and it is possible to suppress plastic deformation of the convex portion 62a of the concave-convex surface <NUM> of the welding pin <NUM>.

(<NUM>-<NUM>)
In the scroll compressor <NUM> of the present embodiment, the downgage <NUM> is disposed, so as to interpose the first hole 124a, on both sides of the first hole 124a in the circumferential direction of the cylindrical member <NUM> of the casing <NUM>. The welding pin <NUM> has the first length L in the radial direction of the cylindrical member <NUM> of the casing <NUM>. In other words, the welding pin <NUM> has the first length L in the press-fitting direction. In the radial direction of the casing <NUM>, the region where the downgage <NUM> exists and the region where the welding pin <NUM> exists overlap with each other in a range of <NUM>% or more of the first length L.

In the scroll compressor <NUM> of the present embodiment, in the radial direction of the casing <NUM>, the region where the downgage <NUM> exists and the region where the welding pin <NUM> exists overlap with each other in the range of <NUM>% or more of the first length L of the welding pin <NUM>. Therefore, plastic deformation of the convex portion 62a of the concave-convex surface <NUM> of the welding pin <NUM> is easily suppressed when the welding pin <NUM> is thermally expanded.

Modification examples of the above-described embodiment will be described below. Alternatively, the following modification examples may appropriately be combined insofar as there are no inconsistencies.

In the above embodiment, the compressor has been described by taking the scroll compressor <NUM> as an example, but the type of compressor is not limited to the scroll compressor. The configuration of the present disclosure in which the low rigidity region is provided in the support that supports the bearing that rotatably supports the drive shaft is widely applicable to a compressor in which a hole for press-fitting a welding pin is provided in a support, and the welding pin and a casing are fixed by welding. For example, the compressor of the present disclosure may be a rotary compressor.

In the above embodiment, the thin portion 128a is provided on both sides of the first hole 124a of the main body portion <NUM> of the housing <NUM> in the circumferential direction of the cylindrical member <NUM> of the casing <NUM>. On the other hand, the thin portion 128a is not provided on both sides of the second hole 124b (the hole disposed above the first hole 124a) of the main body portion <NUM> of the housing <NUM>. However, the present invention is not limited thereto, and for example, the thin portion 128a may be provided on both sides of the adjacent portion of the second hole 124b of the main body portion <NUM> of the housing <NUM> in the circumferential direction of the cylindrical member <NUM> of the casing <NUM> by increasing a depth of the downgage <NUM>. With this configuration, similarly, when the welding pin <NUM> press-fitted into the second hole 124b is thermally expanded at the time of welding to the casing <NUM>, the housing <NUM> can be deformed to suppress plastic deformation of the convex portion 62a of the concave-convex surface <NUM> of the welding pin <NUM>.

In the above embodiment, in the main body portion <NUM> of the housing <NUM>, the holes <NUM> are provided at two positions in the axial direction of the drive shaft <NUM> at each of four locations in the circumferential direction of the cylindrical member <NUM> of the casing <NUM>.

However, the present invention is not limited thereto, and for example, in the main body portion <NUM> of the housing <NUM>, the hole <NUM> may be provided at only one position at each of four locations in the circumferential direction of the cylindrical member <NUM> of the casing <NUM>. For example, the welding pins <NUM> press-fitted into the second hole 124b and the second hole 124b in the above embodiment may be omitted.

Alternatively, in the main body portion <NUM> of the housing <NUM>, three or more holes <NUM> may be provided at each of four locations in the circumferential direction of the cylindrical member <NUM> of the casing <NUM>. In this case, at least a part of the periphery of the adjacent portion adjacent to the hole <NUM> disposed closest to the bearing metal <NUM> in the axial direction of the drive shaft <NUM> among the holes <NUM> is preferably provided with the low rigidity region having lower rigidity than the adjacent portion.

In the above embodiment, in the main body portion <NUM> of the housing <NUM>, the holes <NUM> are provided at two positions in the axial direction of the drive shaft <NUM> so that the holes <NUM> are arrayed in the axial direction of the drive shaft <NUM> at each of four locations in the circumferential direction of the cylindrical member <NUM> of the casing <NUM>.

However, the present invention is not limited thereto, and for example, the hole <NUM> disposed on the lower side of the main body portion <NUM> of the housing <NUM> (the first hole 124a in the above embodiment) and the hole <NUM> disposed on the upper side of the main body portion <NUM> of the housing <NUM> (the second hole 124b in the above embodiment) may be disposed at different positions in the circumferential direction of the cylindrical member <NUM> of the casing <NUM>.

In the above embodiment, the thin portion 128a of the low rigidity region <NUM> is formed by forming the downgage <NUM> closer to the center axis O of the casing <NUM> than the outer surface <NUM> of the housing <NUM>. However, a method of forming the thin portion 128a is not limited thereto.

For example, as in a housing <NUM> illustrated in <FIG>, a thin portion 228a may be provided by providing a groove <NUM> on the outer surface <NUM> of the main body portion <NUM> of the housing <NUM> instead of the downgage <NUM>. Here, the groove <NUM> is provided on both sides of the hole <NUM> (the first hole 124a and the second hole 124b) in the circumferential direction of the cylindrical member <NUM> of the casing <NUM> so as to interpose the hole <NUM>. The groove <NUM> is recessed radially inward of the casing <NUM> with respect to the outer surface <NUM> of the main body portion <NUM> and extends along the axial direction of the drive shaft <NUM>.

As a result of forming the groove <NUM>, a thickness of the thin portion 228a in the radial direction of the cylindrical member <NUM> of the casing <NUM> (a thickness of a portion where a member exists between the outer surface <NUM> of the main body portion <NUM> and the crank chamber <NUM>) is smaller than the minimum thickness K of the adjacent portion <NUM>.

In the thin portion 228a of the present embodiment, a thickness from a bottom portion of the groove <NUM> to a position where the bottom portion <NUM> of the hole <NUM> exists is smaller than the depth A of the hole <NUM> in the radial direction of the cylindrical member <NUM> of the casing <NUM>. In short, in the adjacent portion <NUM>, in the radial direction of the cylindrical member <NUM> of the casing <NUM>, a member having the thickness A exists from the position where the bottom portion <NUM> of the hole <NUM> to the outer surface <NUM> of the main body portion <NUM>, whereas a thickness from the position where the bottom portion <NUM> of the hole <NUM> exists to the bottom portion of the groove <NUM> of the thin portion 228a is smaller than the thickness A. In other words, in the radial direction of the cylindrical member <NUM> of the casing <NUM>, the thickness of the thin portion 228a existing further on an outer side than the position of the bottom portion <NUM> of the hole <NUM> is thinner than the depth A of the hole <NUM> by a depth of the groove <NUM> in the radial direction of the cylindrical member <NUM> of the casing <NUM>.

In the radial direction of the cylindrical member <NUM> of the casing <NUM>, a region where the groove <NUM> exists and the region where the welding pin <NUM> press-fitted into the hole <NUM> exists preferably overlap with each other in a range of <NUM>% or more of the length of the welding pin <NUM> press-fitted into the hole <NUM> in the radial direction of the cylindrical member <NUM> of the casing <NUM> (in other words, the length L of the welding pin <NUM> in the press-fitting direction). Here, it is assumed that the welding pin <NUM> is press-fitted to a position where the welding pin abuts against the bottom portion <NUM> of the hole <NUM>.

The low rigidity region <NUM> provided in the main body portion <NUM> of the housing <NUM> of the present modification includes the void portion 128b in addition to the thin portion 228a. Description of the void portion 128b is omitted since the void portion 128b is similar to that in the above embodiment.

In a case where the thin portion 228a and the void portion 128b are provided in the main body portion <NUM> as in the present modification example, as well as in the above embodiment, when the welding pin <NUM> is thermally expanded at the time of welding to the casing <NUM>, the housing <NUM> can be deformed to suppress plastic deformation of the convex portion 62a of the concave-convex surface <NUM> of the welding pin <NUM>. As a result of suppressing the plastic deformation of the convex portion 62a of the concave-convex surface <NUM> of the welding pin <NUM>, a relatively large holding force of the welding pin <NUM> after welding can be maintained.

Further, in the present modification example, by forming the groove <NUM> extending to a side of the second hole 124b to provide the thin portion 228a, when the welding pin <NUM> press-fitted into the second hole 124b is thermally expanded at the time of welding to the casing <NUM>, the housing <NUM> can be deformed to suppress plastic deformation of the convex portion 62a of the concave-convex surface <NUM> of the welding pin <NUM>. As a result, as for not only the welding pin <NUM> press-fitted into the first hole 124a but also the welding pin <NUM> press-fitted into the second hole 124b, a relatively large holding force of the welding pin <NUM> after welding can be maintained.

For example, in the housing of the scroll compressor <NUM>, as the low rigidity region, the thin portion 128a formed by providing the downgage <NUM> as in the above embodiment and the thin portion 228a formed by providing the groove <NUM> as in the present modification example may be mixed.

Further, on the outer surface <NUM> of the main body portion <NUM> of the housing <NUM>, for example, a groove <NUM> may further be provided along the circumferential direction of the cylindrical member <NUM> of the casing <NUM> between the first hole 124a and the second hole 124b (refer to a broken line in <FIG>). By providing the groove <NUM> in this manner, plastic deformation of the convex portion 62a of the concave-convex surface <NUM> of the welding pin <NUM> press-fitted into the first hole 124a and the second hole 124b tends to be further suppressed.

In the above embodiment, the housing <NUM> is fixed by press fitting and welding. However, the present invention is not limited thereto, and for example, the housing <NUM> may be fixed to the casing <NUM> only by welding (only by welding of the welding pin <NUM> press-fitted into the hole <NUM> of the main body portion <NUM> and the casing <NUM>).

In the above embodiment, the vertical scroll compressor in which the axial direction of the drive shaft <NUM> is a vertical direction is described as an example, but the compressor may be a horizontal compressor in which the axial direction of the drive shaft <NUM> is a horizontal direction.

In the scroll compressor <NUM> of the above embodiment, when the first hole 124a is viewed from a position just facing the first hole 124a, the low rigidity region <NUM> is provided in the region at <NUM>° or more around the center of the first hole 124a, but the present invention is not limited thereto. The low rigidity region <NUM> may be provided in a region smaller than the region at <NUM>° around the center of the first hole 124a. However, by providing, the low rigidity region <NUM> in the region at <NUM>° or more around the center of the first hole 124a when the first hole 124a is viewed from a position just facing the first hole 124a, plastic deformation of the convex portion 62a of the concave-convex surface <NUM> of the welding pin <NUM> press-fitted into the first hole 124a tends to be particularly suppressed.

In the above embodiment, the housing <NUM> and the lower bearing housing <NUM> support the bearing metal <NUM> and the bearing metal <NUM> as examples of bearings, respectively, but the present invention is not limited thereto. For example, the housing <NUM> and the lower bearing housing <NUM> may support roller bearings such as ball bearings instead of the bearing metals <NUM> and <NUM>.

In the above embodiment, the scroll compressor of the present disclosure is described by taking, as an example, a case where the welding pin <NUM> has the concave-convex surface <NUM> having a concave-convex shape on the outer periphery. However, for example, the welding pin before press-fitting used in the scroll compressor of the present disclosure may be a cylindrical welding pin <NUM> not having the concave-convex surface <NUM>. In other words, as illustrated in <FIG>, for example, the welding pin <NUM> before press-fitting may have a circular shape when viewed along the press-fitting direction.

A scroll compressor according to the modification example J described herein is similar to the scroll compressor of the above embodiment except for the welding pin <NUM>.

In short, a configuration similar to the configuration described in the above embodiment will be described using the same reference signs as those used to describe the above embodiment. A scroll compressor <NUM> of the modification example J includes a motor <NUM>, a compression mechanism <NUM>, a drive shaft <NUM>, a housing <NUM>, a casing <NUM>, and a welding pin <NUM>. The drive shaft <NUM> transmits a driving force of the motor <NUM> to the compression mechanism <NUM>. The housing <NUM> supports a bearing metal <NUM>, provided in an upper bearing housing <NUM>, that rotatably supports the drive shaft <NUM>. At least one hole <NUM> is formed in an outer surface <NUM> of a main body portion <NUM> of the housing <NUM>. The casing <NUM> accommodates the drive shaft <NUM> and the housing <NUM> therein. The casing <NUM>, in particular, a cylindrical member <NUM>, has a cylindrical shape. The welding pin <NUM> is press-fitted into the hole <NUM> of the housing <NUM> and is welded and fixed to the casing <NUM>. A low rigidity region <NUM> is provided at least a part of a periphery of an adjacent portion adjacent to the hole <NUM> of the housing <NUM>, particularly in the present embodiment, at least a part of a periphery of an adjacent portion <NUM> adjacent to a first hole 124a. The low rigidity region <NUM> has lower rigidity than the adjacent portion <NUM>. The low rigidity region <NUM> includes a thin portion 128a having a smaller thickness in a radial direction of the casing <NUM> than the adjacent portion <NUM>.

With such a configuration, in the scroll compressor <NUM> of the modification example J, the housing <NUM> can deform when the welding pin <NUM> is thermally expanded during welding, and excessive plastic deformation of the welding pin <NUM> can be suppressed. As a result of suppressing the plastic deformation of the welding pin <NUM>, a relatively large holding force of the welding pin <NUM> after welding can be maintained.

Although not described in detail herein, the scroll compressor <NUM> according to the modification example J preferably has the characteristics described in (<NUM>-<NUM>) to (<NUM>-<NUM>) of the above embodiment except that the welding pin <NUM> does not have the concave-convex surface.

The present disclosure is widely applicable and useful to a compressor in which a welding pin is press-fitted into a hole on an outer surface of a support that supports a bearing, and the welding pin and a casing are welded and fixed.

Claim 1:
A compressor (<NUM>) comprising:
an actuator (<NUM>);
a compression mechanism (<NUM>);
a drive shaft (<NUM>) configured to transmit a driving force of the actuator to the compression mechanism;
a support (<NUM>, <NUM>) supporting a bearing (<NUM>) configured to rotatably support the drive shaft, the support (<NUM>, <NUM>) having at least one hole (<NUM>) formed in an outer surface (<NUM>) thereof;
a casing (<NUM>) having a cylindrical shape and accommodating the drive shaft and the support therein; and
a welding pin (<NUM>, <NUM>) being press-fitted into the hole of the support and welded and fixed to the casing,
wherein
a low rigidity region (<NUM>, <NUM>) is provided at least a part of a periphery of an adjacent portion (<NUM>) adjacent to the hole of the support, the low rigidity region has lower rigidity than the adjacent portion, and
the low rigidity region includes a thin portion (128a, 228a) having a smaller thickness in a radial direction of the casing than the adjacent portion wherein,
in the low rigidity region (<NUM>), a downgage (<NUM>) is formed closer to a center axis (O) of the casing than the outer surface of the support.,
characterized in that the downgage is disposed, so as to interpose the hole, on both sides of the hole in a circumferential direction of the casing,
the welding pin has a first length (L) in a radial direction of the casing, and,
in the radial direction of the casing, a region where the downgage exists and a region where the welding pin exists overlap with each other in a range of <NUM>% or more of the first length.