EP4678916A1

EP4678916A1 - Compressor

Info

Publication number: EP4678916A1
Application number: EP24770462.0A
Authority: EP
Inventors: Taichi Tateishi; Akihiro KANAI; Yogo Takasu; Masahiro Taniguchi; Yoshiki Kobayashi
Original assignee: Mitsubishi Heavy Industries Thermal Systems Ltd
Current assignee: Mitsubishi Heavy Industries Thermal Systems Ltd
Priority date: 2023-03-16
Filing date: 2024-02-21
Publication date: 2026-01-14
Also published as: EP4678916A4; JP2024131733A; WO2024190349A1

Abstract

Provided is a compressor that can suppress increase in an oil circulation rate. The present invention is provided with: a housing (33) into which a refrigerant is introduced; a compression mechanism that is accommodated in the housing (33) and compresses a refrigerant (R); and an electric motor (100) that is accommodated in the housing (33) and rotationally drives the compression mechanism via a drive shaft (95) extending along an axis (X). The electric motor (100) has a stator core (111) in which a plurality of slots (111s) are provided in the circumferential direction, and coil parts (112) provided in the slots (111s), and has gaps (112g) formed between coil ends (112e) of the coil parts (112) protruding from the slots (111s) of the stator core (111) in the direction of the axis (X), to thereby form distributed winding. The electric motor is provided with a blocking part (131) for blocking the flow of the refrigerant from an outer region in the radial direction of the coil ends (112e) to an inner region via the gaps (112g).

Description

Technical Field

The present disclosure relates to a compressor driven by an electric motor.

Background Art

For example, a hermetic compressor includes a housing that defines a hermetic space, a compression mechanism that is accommodated in the housing and compresses a refrigerant, and an electric motor that is accommodated in the housing and drives the compression mechanism.
In such a hermetic compressor, for example, as disclosed in PTL 1, there is a case where it is desirable to reduce the oil circulation rate.

Citation List

Patent Literature

[PTL 1] Japanese Unexamined Patent Application Publication No. 2007-100512

Summary of Invention

Technical Problem

In a case where a stator having distributed winding is adopted for an electric motor that drives a compression mechanism, a refrigerant containing mist-like oil (lubricant) may flow into a region on the inner side of a coil end via a gap formed in a circumferential direction between the coil ends.
In a case where a counterweight attached to a rotor is present in a region on the inner side of the coil end, when the refrigerant enters the region, the refrigerant containing oil is stirred by the counterweight, the oil is wound up, and flows into the compression mechanism, so that there is a possibility that the oil circulation rate may increase.
The present disclosure has been made in view of such circumstances, and an object of the present disclosure is to provide a compressor that can prevent an increase in an oil circulation rate.

Solution to Problem

In order to solve the above problems, a compressor of the present disclosure adopts the following means.
A compressor according to an aspect of the present disclosure includes a housing into which a refrigerant is guided, a compression mechanism that is accommodated in the housing and compresses the refrigerant, and an electric motor that is accommodated in the housing and rotationally drives the compression mechanism via a drive shaft extending along an axis, in which the electric motor includes a stator core in which a plurality of slots are provided in a circumferential direction, and a coil part provided in each of the slots, and has distributed winding in which gaps are formed between respective coil ends of the coil parts protruding in a direction of the axis from respective slots of the stator core, and the compressor further includes a blocking part that blocks a flow of the refrigerant from a region on an outer side to a region on an inner side of the coil end in a radial direction via the gap. Advantageous Effects of Invention
According to the present disclosure, it is possible to prevent an increase in the oil circulation rate.

Brief Description of Drawings

FIG. 1 is a longitudinal cross-sectional view taken along an axis of a compressor according to an embodiment of the present disclosure.
FIG. 2 is a cross-sectional view taken along a cutting line II-II in FIG. 1 (Example 1).
FIG. 3 is a front view of an electric motor included in the compressor according to the embodiment of the present disclosure (after a blocking part is mounted).
FIG. 4 is a front view of the electric motor included in the compressor according to the embodiment of the present disclosure (when the blocking part is mounted).
FIG. 5 is a cross-sectional view taken along the cutting line II-II illustrated in FIG. 1 (Example 2).
FIG. 6 is a partially enlarged view of the vicinity of a coil end of the compressor illustrated in FIG. 1 (Example 3).
FIG. 7 is a cross-sectional view taken along the cutting line II-II illustrated in FIG. 1 (Modification Example 1).

Description of Embodiments

Hereinafter, a compressor according to an embodiment of the present disclosure will be described with reference to the drawings.

[Regarding Structure of Compressor]

For example, a compressor 11 is a hermetic scroll compressor.
The compressor 11 constitutes a refrigeration cycle together with a condenser, an expansion valve, an evaporator, a refrigerant pipe, and the like (not illustrated).
The compressor 11 may be any compressor that includes a scroll compression mechanism, and may be, for example, a compressor (scroll rotary compressor) that includes a compression mechanism in which a scroll compression mechanism and a rotary compression mechanism are combined.
As illustrated in FIG. 1, the compressor 11 includes a housing 33 having a hermetic space inside, a discharge cover 40 that divides the hermetic space, a compression mechanism 60 that compresses the refrigerant R, a drive shaft 95 that causes an orbiting scroll 80 of the compression mechanism 60 to perform a revolving and orbiting motion, an electric motor 100 that drives the drive shaft 95, and a blocking part 130.
The hermetic space is formed inside the housing 33 by an upper housing 33A, an intermediate housing 33B, and a lower housing (not illustrated).
The upper housing 33A and the intermediate housing 33B are connected to each other in a state where an outer peripheral end portion of the discharge cover 40 is interposed therebetween.
That is, the hermetic space inside the housing 33 is divided in the direction of an axis X by the discharge cover 40. In the divided hermetic spaces, the hermetic space formed on the upper housing 33A side is a discharge chamber 53, and the hermetic space formed on the intermediate housing 33B side is a suction chamber 55.
A discharge pipe 31 for discharging the refrigerant R is provided on an upper wall of the upper housing 33A and allows the discharge chamber 53 and the outside of the upper housing 33A (housing 33) to communicate with each other.
A refrigerant pipe is connected to the discharge pipe 31, and the refrigerant R discharged from the discharge pipe 31 is configured to be guided to the condenser.
A suction port 33B1 is formed in a side wall of the intermediate housing 33B, and a suction pipe 32 for sucking the refrigerant R is provided in the suction port 33B1, and allows the suction chamber 55 and the outside of the intermediate housing 33B (housing 33) to communicate with each other.
A refrigerant pipe is connected to the suction pipe 32, and the refrigerant R evaporated in the evaporator is configured to be guided to the suction chamber 55.
The suction chamber 55 is provided with a compression mechanism 60 that compresses the refrigerant R, a drive shaft 95 that transmits a rotational force from the electric motor 100 to the compression mechanism 50, a support member 97 that pivotally supports the drive shaft 95, and an electric motor 100 that rotationally drives the drive shaft 95.
The compression mechanism 60 includes a fixed scroll 70 in which a spiral fixed wall body 75 is erected on a fixed end plate 71 and an orbiting scroll 80 in which a spiral orbiting wall body 85 is erected on an orbiting end plate 81.
In the fixed scroll 70 and the orbiting scroll 80, the fixed wall body 75 and the orbiting wall body 85 mesh with each other to form the compression chamber 61. A tip gap is set in consideration of thermal expansion of each wall body between a tooth tip of the fixed wall body 75 and a tooth bottom of the orbiting end plate 81 and between a tooth tip of the orbiting wall body 85 and a tooth bottom of the fixed end plate 71.
The fixed scroll 70 is fixed to the support member 97 by a fixing portion 74 formed at an outer peripheral end portion of the fixed end plate 71. Since the support member 97 is fixed to the intermediate housing 33B, the fixed scroll 70 is fixed to the intermediate housing 33B via the support member 97.
The "radial direction" and the "circumferential direction" referred to herein are directions with respect to the axis X of the fixed scroll 70.
The orbiting scroll 80 is configured to perform revolving and orbiting motion around the axis X of the fixed scroll 70 by the drive shaft 95 and a rotation prevention mechanism (for example, an Oldham link).
The discharge cover 40 is disposed above the fixed scroll 70 (on the back surface side of the fixed end plate 71), and defines the back pressure chamber 54 together with the back surface of the fixed end plate 71.
A discharge port 72 through which the compression chamber 61 and the back pressure chamber 54 communicate with each other is formed in the fixed end plate 71. In addition, a discharge port 41 (different from the discharge port 72 of the fixed end plate 71) through which the back pressure chamber 54 and the discharge chamber 53 communicate with each other is formed in the discharge cover 40.
That is, the compression chamber 61 and the discharge chamber 53 communicate with each other via the discharge port 72, the back pressure chamber 54, and the discharge port 41.
The high-pressure refrigerant R compressed by the compression mechanism 60 is guided to the discharge chamber 53. On the other hand, the low-pressure refrigerant R is guided to the suction chamber 55 via the suction pipe 32. In addition, the low-pressure refrigerant R guided to the suction chamber 55 is sucked into the compression mechanism 60.
Therefore, the compressor 11 of the present embodiment has a low-pressure housing structure in which the discharge cover 40 serves as a partition between the high-pressure side (the discharge chamber 53) and the low-pressure side (the suction chamber 55), and the drive shaft 95, the support member 97, and the electric motor 100 are disposed on the low-pressure side. A partition element that partitions the high-pressure side and the low-pressure side does not necessarily need to be the discharge cover 40, and may be partitioned by, for example, the fixed scroll 70.
In the back pressure chamber 54, a retainer 93 that regulates a reed valve 92 and a movable range of the reed valve 92 is provided at an outlet portion of the discharge port 72.

[Regarding Electric Motor and Blocking Part]

As illustrated in FIGS. 1 to 3, the electric motor 100 includes a stator 110 that has distributed winding and is fixed to an intermediate housing 33B, and a rotor 120 that is fixed to the drive shaft 95 and rotates around an axis X with respect to the stator 110.
The stator 110 includes a stator core 111 and a coil part 112.
The stator core 111 is a laminate (laminated steel plate) of thin electromagnetic steel plates, and is fixed to the intermediate housing 33B. A plurality of slots 111s extending along the direction of the axis X are formed in the stator core 111. The plurality of slots 111s are provided at equal angular intervals in the circumferential direction.
The coil part 112 is formed of a linear conductor (for example, an enamel wire) wound around the slot 111s. The coil part 112 forms a coil end 112e that protrudes along the direction of the axis X from both end surfaces of the stator core 111 in the direction of the axis X. For the sake of description, the coil end 112e is illustrated in cross-hatching in FIG. 1.
As illustrated in FIGS. 2 and 3, a gap 112g is formed between the coil end 112e immediately after the coil end 112e jumps out from one slot 111s and the coil end 112e immediately after the coil end 112e jumps out from another slot 111s adjacent to the one slot 111s in the circumferential direction, and at a position adjacent to an end surface of the stator core 111 in the direction of the axis X.
The gaps 112g are formed at equal angular intervals in the circumferential direction, similar to the slots 111s, and are formed in the number corresponding to the number of slots 111s.
The gap 112g is a portion specific to an electric motor 100 (stator 110) having distributed winding, and is generally not present in an electric motor 100 (stator 110) having concentrated winding.
As illustrated in FIGS. 1 and 2, the rotor 120 is fixed to an outer peripheral surface of the drive shaft 95.
Counterweights 121 having a semicircular shape in the circumferential direction are attached to both end surfaces of the rotor 120 in the direction of the axis X. The counterweight 121 rotates around the axis X together with the rotor 120.
In the electric motor 100 configured as described above, the refrigerant R may flow from a region on the outer side (hereinafter, simply referred to as an "outer region") into a region on the inner side (hereinafter, simply referred to as an "inner region") of the coil end 112e via the gap 112g formed between one coil end 112e and the other coil end 112e in the suction chamber 55.
In particular, in a case where the coil end 112e (upper coil end 112e in FIG. 1) of the stator 110 is disposed to face the suction port 33B1 provided in the side wall of the intermediate housing 33B, in other words, in a case where the upper coil end 112e and the suction port 33B1 are in an overlapping range in the direction of the axis X (height direction), the refrigerant R taken in from the suction port 33B1 is likely to directly flow from the outer region into the inner region via the gap 112g.
There is a case where it is not preferable that the refrigerant R flows into the inner region of the coil end 112e.
For example, in a case where the counterweight 121 is present in the inner region, when the refrigerant R enters the inner region, the refrigerant R containing mist-like oil is stirred by the counterweight 121, the oil is wound up, and flows into the compression mechanism 60, so that there is a possibility that the oil circulation rate may increase.
The compressor 11 according to the present embodiment is provided with a blocking part 130 that blocks the flow of the refrigerant R so that the refrigerant R does not flow from the outer region into the inner region via each of the gaps 112g. By providing the blocking part 130, the amount of the refrigerant R guided to the inner region can be reduced, and the amount of oil flowing into the compression mechanism 60 due to the winding by the counterweight 121 can be reduced, so that an increase in the oil circulation rate can be prevented.
Hereinafter, the blocking part 130 will be described as an example of Examples 1 to 3 and Modification Examples 1 to 3.

As illustrated in FIGS. 1 to 3, the blocking part 130 (blocking part 131) of Example 1 is an object that covers the outer peripheral surface of the coil end 112e while being in close contact with the outer peripheral surface to cover the gap 112g.
For example, the blocking part 131 is an annular band-shaped body having insulating properties and centered on the axis X.
For example, the band-shaped body is a resin film.
For example, the resin film is a heat shrinkable film that shrinks by heating.
As illustrated in FIG. 4, for example, the heat shrinkable film serving as the blocking part 131 is an annular member having an inner diameter larger than the maximum diameter portion of the coil end 112e.
The heat shrinkable film is disposed at a height position overlapping the gap 112g (indicated by a dashed double-dotted line in FIG. 4), and is heated to be shrunk and in close contact with the outer peripheral surface of the coil end 112e (refer to FIG. 3). As a result, the heat shrinkable film covers the gap 112g.
In addition, the band-shaped body is not limited to the resin film, and may be a string such as a rubber band and a binding string, or a string obtained by solidifying the string with a varnish.

As illustrated in FIG. 5, the blocking part 130 (blocking part 132) of Example 2 is an object that fills all the gaps 112g.
The blocking part 132 has insulating properties.
The blocking parts 132 filled in each of the gaps 112g may be independent of each other, or may be integrated with a part or all of the blocking parts 132.
In addition, the gap 112g may be filled with the blocking part 132, and then the blocking part 131 may be provided on the outer peripheral surface of the coil end 112e.

As illustrated in FIG. 6, the blocking part 130 (blocking part 133) of Example 3 is an annular baffle plate centered on the axis X, which is provided between the intermediate housing 33B and the outer peripheral surface of the coil end 112e in the radial direction and is not in contact with the coil end 112e.
The blocking part 133 has insulating properties.
The baffle plate serving as the blocking part 131 overlaps with the gap 112g in the height direction.
The baffle plate may be attached to the stator core 111 or may be attached to the intermediate housing 33B. In addition, the baffle plate may be attached to a portion other than the above-described portions.
The baffle plate is not in contact with the coil end 112e, but it is sufficient as long as the baffle plate is separated from the coil end 112e by at least a distance at which electrical insulation can be achieved (for example, 1.6 mm or more in the radial direction).

In Example 1 and Example 3, the blocking parts 131 and 133 are formed in an annular shape, or in Example 2, all the gaps 112g are filled with the blocking part 132, so that the circulation of the refrigerant R in all the gaps 112g is blocked.
However, the blocking part 130 may be provided to block the circulation of the refrigerant R in at least the gap 112g in a range facing the suction port 33B1, in other words, in the gap 112g in a range overlapping the suction port 33B1 in the circumferential direction.
When the blocking part 130 is provided in the range as described above, the refrigerant R taken in from the suction port 33B1 collides with the blocking part 130 in a case where the coil end 112e and the suction port 33B1 are disposed to face each other. The oil in the refrigerant R is separated by the collision of the refrigerant R with the blocking part 130.
In addition, when the blocking part 130 is provided in the range as described above, the refrigerant R taken in from the suction port 33B1 flows along the blocking part 130 in a case where the coil end 112e and the suction port 33B1 are disposed to face each other. The refrigerant R flows along the blocking part 130 to have a velocity component in the circumferential direction, and the oil in the refrigerant R is centrifuged.
As illustrated in FIG. 7, for example, the range in which the blocking part 130 is provided is ± α degrees in the circumferential direction from a position facing a central portion of the suction port 33B1. For example, α is 60 degrees or more, preferably 90 degrees or more.
In a case where the coil end 112e and the suction port 33B1 are disposed to face each other, it goes without saying that the effect of collision separation and/or the effect of centrifugal separation can be obtained even when the blocking parts 131 and 133 are annular or all the gaps 112g are filled with the blocking part 132.
In addition, in terms of reducing the amount of refrigerant R flowing into the inner region of the coil end 112e, even when the blocking part 130 is not provided in the gap 112g in the range facing the suction port 33B1, the effect can at least be achieved by providing the blocking part 130 in the gap 112g in the range not facing the suction port 33B1 in the circumferential direction.

For example, as illustrated in FIG. 1, it is preferable that the outer peripheral surface of the blocking part 130 is inclined to approach the axis X as going downward in the longitudinal section along the axis X.
As a result, the refrigerant R containing oil is unlikely to be wound up, and the oil circulation rate can be reduced.

In the above-described example (including the modification example), the blocking part 130 is provided in the upper coil end 112e. However, in addition to or instead of the blocking part 130, the blocking part 130 may be provided in the lower coil end 112e.
In addition, the blocking part 130 may be disposed in the inner region of the coil end 112e.

In the above-described example (including the modification example), the blocking part 130 is configured to block the circulation of the low-pressure refrigerant R guided via the suction port 33B1 connected to the suction pipe 32. However, the blocking part 130 may be configured to block the circulation of the refrigerant R other than the low-pressure refrigerant R.
For example, the blocking part 130 may be configured to block the intermediate-pressure gas, the injection gas, or the return gas from a capacity control mechanism.
Here, the term "intermediate-pressure gas" refers to a gas (refrigerant) compressed one or more times in a compression mechanism that compresses the refrigerant in a plurality of times. In addition, the term "injection gas" refers to a gas that is once radiated from compressed gas (refrigerant) and reheated. In addition, the term "return gas from the capacity control mechanism" refers to a gas that is returned from the compression mechanism to the intermediate housing 33B before being compressed or immediately after the start of compression, among the gas (refrigerant) that enters the compression mechanism.
In a case where the compressor 11 is a scroll rotary compressor, the blocking part 130 targets the intermediate-pressure gas or the injection gas.
According to the present embodiment, the following effects are achieved.
Since the compressor 11 includes the blocking parts 130 (131, 132, 133), the amount of the refrigerant R guided to the inner region of the coil end 112e can be reduced.
There is a case where it is not preferable that the refrigerant R guided to the outer region of the coil end 112e flows into the inner region of the coil end 112e. For example, in a case where the counterweight 121 attached to the rotor 120 is present in the inner region of the coil end 112e, when the refrigerant R enters the region, the refrigerant R containing mist-like oil (lubricant) is stirred by the counterweight 121, the oil is wound up, and flows into the compression mechanism 60, so that there is a possibility that the oil circulation rate may increase.
Therefore, by reducing the amount of the refrigerant R guided to the inner region of the coil end 112e by the blocking part 130, the amount of the oil flowing into the compression mechanism 60 due to the winding is reduced, and the phenomenon in which the oil circulation rate increases can be prevented.
In addition, since the blocking part 131 is an object that covers the gap 112g by covering the outer peripheral surface of the coil end 112e while being in close contact with the outer peripheral surface, the flow of the refrigerant R can be reliably blocked with a simple structure.
In addition, since the blocking part 132 is an object that fills the gap 112g, the flow of the refrigerant R can be reliably blocked with a simple structure.
In addition, since the blocking part 133 serves as a baffle plate, the flow of the refrigerant can be blocked with a simple structure. In addition, the blocking part 133 can be easily attached.
In addition, by providing the blocking part 130 at least in a range facing the suction port 33B1, the flow of the refrigerant R from the outer region to the inner region of the coil end 112e via the gap 112g can be efficiently blocked.
In addition, the oil in the refrigerant R is separated by the collision of the refrigerant R taken in from the suction port 33B1 with the blocking part 130, and the oil circulation rate can be reduced.
In addition, the refrigerant R taken in from the suction port 33B1 flows along the blocking part 130, so that the refrigerant R has a velocity component in the circumferential direction, the oil in the refrigerant R is centrifuged, and the oil circulation rate can be reduced.
In addition, in a case where the blocking part 130 is inclined to approach the axis X as going downward in the longitudinal section along the axis X, the refrigerant R containing oil is unlikely to be wound up, and the oil circulation rate can be reduced.
The compressor according to the embodiment of the present disclosure described above is understood as follows, for example.
A compressor (11) according to a first aspect of the present disclosure includes: a housing (33) into which a refrigerant (R) is guided, a compression mechanism (60) that is accommodated in the housing and compresses the refrigerant, and an electric motor (100) that is accommodated in the housing and rotationally drives the compression mechanism via a drive shaft (95) extending along an axis (X), in which the electric motor includes a stator core (111) in which a plurality of slots (111s) are provided in a circumferential direction, and a coil part (112) provided in each of the slots, and has distributed winding in which gaps are formed between respective coil ends (112e) of the coil parts protruding in a direction of the axis from respective slots of the stator core, and the compressor further includes a blocking part (130) that blocks a flow of the refrigerant from a region on an outer side to a region on an inner side of the coil end in a radial direction via the gap.
According to the compressor in the present aspect, the electric motor has distributed winding in which the gap is formed between each of the coil ends, and the compressor includes the blocking part that blocks the flow of the refrigerant from the region on the outer side to the region on the inner side of the coil end in the radial direction via the gap. Therefore, the amount of the refrigerant guided to the region on the inner side of the coil end can be reduced.
There is a case where it is not preferable that the refrigerant guided to the region on the outer side of the coil end flows into a region on the inner side of the coil end. For example, in a case where a counterweight attached to the rotor is present in a region on the inner side of the coil end, when the refrigerant enters the region, the refrigerant containing mist-like oil (lubricant) is stirred by the counterweight, the oil is wound up, and flows into the compression mechanism, so that there is a possibility that the oil circulation rate may increase.
Therefore, by reducing the amount of the refrigerant guided to the region on the inner side of the coil end by the blocking part, the amount of the oil flowing into the compression mechanism due to the winding can be reduced, and the phenomenon in which the oil circulation rate increases can be prevented.
In the compressor according to a second aspect of the present disclosure, in the first aspect, the blocking part (131) is an object that covers the gap by covering an outer peripheral surface of the coil end while being in close contact with the outer peripheral surface.
According to the compressor in the present aspect, since the blocking part is an object that covers the gap by covering the outer peripheral surface of the coil end while being in close contact with the outer peripheral surface, the flow of the refrigerant R can be reliably blocked with a simple structure.
In the compressor according to a third aspect of the present disclosure, in the first aspect, the blocking part (132) is an object that fills the gap.
According to the compressor in the present aspect, since the blocking part is the object that fills the gap, the flow of the refrigerant can be reliably blocked with a simple structure.
In the compressor according to a fourth aspect of the present disclosure, in the first aspect, the blocking part (133) is a baffle plate that is provided between the housing and the coil end in the radial direction and that is not in contact with the coil end.
According to the compressor in the present aspect, the blocking part is the baffle plate that is provided between the housing and the coil end in the radial direction and that is not in contact with the coil end. Therefore, the flow of the refrigerant can be blocked with a simple structure. In addition, the blocking part can be easily attached.
In the compressor according to a fifth aspect of the present disclosure, in any one of the first to fourth aspects, the blocking part is provided at least in a range facing a suction port (33B1) provided in the housing and that takes in the refrigerant into the housing.
According to the compressor in the present aspect, since the blocking part is provided at least in a range facing the suction port, the flow of the refrigerant from the region on the outer side to the region on the inner side of the coil end can be efficiently blocked via the gap.
In addition, the oil in the refrigerant is separated by the collision of the refrigerant taken in from the suction port with the blocking part, and the oil circulation rate can be reduced.
In addition, the refrigerant taken in from the suction port flows along the blocking part, so that the refrigerant has a velocity component in the circumferential direction, the oil in the refrigerant is centrifuged, and the oil circulation rate can be reduced.
In the compressor according to a sixth aspect of the present disclosure, in the fifth aspect, the blocking part provided at a position corresponding to the coil end located above among the coil ends above and below the stator core is inclined to approach the axis as going downward in a longitudinal section along the axis.
According to the compressor in the present aspect, since the blocking part is inclined to approach the axis as going downward in the longitudinal section along the axis, the refrigerant containing oil is unlikely to be wound up, and the oil circulation rate can be reduced.

Reference Signs List

11: compressor
31: discharge pipe
32: suction pipe
33: housing
33A: upper housing (housing)
33B: intermediate housing (housing)
33B1: suction port
40: discharge cover
41: discharge port
53: discharge chamber
54: back pressure chamber
55: suction chamber
60: compression mechanism
61: compression chamber
70: fixed scroll
71: fixed end plate
72: discharge port
74: fixing portion
75: fixed wall body
80: orbiting scroll
81: orbiting end plate
85: orbiting wall body
92: reed valve
93: retainer
95: drive shaft
97: support member
100: electric motor
110: stator
111: stator core
111s: slot
112: coil part
112e: coil end
112g: gap (gap in circumferential direction)
120: rotor
121: counterweight
130 (131, 132, 133): blocking part

Claims

A compressor comprising:
a housing into which a refrigerant is guided;

a compression mechanism that is accommodated in the housing and compresses the refrigerant; and

an electric motor that is accommodated in the housing and rotationally drives the compression mechanism via a drive shaft extending along an axis, wherein

the electric motor includes a stator core in which a plurality of slots are provided in a circumferential direction, and a coil part provided in each of the slots, and has distributed winding in which gaps are formed between respective coil ends of the coil parts protruding in a direction of the axis from respective slots of the stator core, and

the compressor further comprises

a blocking part that blocks a flow of the refrigerant from a region on an outer side to a region on an inner side of the coil end in a radial direction via the gap.
The compressor according to Claim 1, wherein
the blocking part is an object that covers the gap by covering an outer peripheral surface of the coil end while being in close contact with the outer peripheral surface.
The compressor according to Claim 1, wherein
the blocking part is an object that fills the gap.
The compressor according to Claim 1, wherein
the blocking part is a baffle plate that is provided between the housing and the coil end in the radial direction and that is not in contact with the coil end.
The compressor according to any one of Claims 1 to 4, wherein
the blocking part is provided at least in a range facing a suction port provided in the housing and that takes in the refrigerant into the housing.
The compressor according to Claim 5, wherein
the blocking part provided at a position corresponding to the coil end located above among the coil ends located above and below the stator core is inclined to approach the axis as going downward in a longitudinal section along the axis.