JP2006118455A - Drive source provided with compression mechanism compressing fluid by using output of electric motor as drive source and compressor provided with compressing mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor of a new structure eliminating a series arrangement of a electric motor and a compression mechanism. <P>SOLUTION: The electric motor 18 rotating a drive shaft 21, a conversion mechanism 28 converting rotary motion of the drive shaft 21 into reciprocating motion in a roughly linear direction, and the compression mechanism connected to the conversion mechanism 28 and provided outside of the electric motor 18 in reference to the drive shaft 21 to enclose the electric motor 18 and provided with a piston 42 reciprocating with operating together with reciprocating motion of the conversion mechanism 28 to suck in compressive fluid from an external circuit and compressing the same and delivering the compressed fluid to an external circuit are provided. Each component is stored in a housing 11. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an electric motor as a drive source having a conversion mechanism that converts the rotational motion of an electric motor into a reciprocating motion of a piston, and a compressor having a piston-type compression mechanism that compresses fluid by its output.

The compression mechanism is a mechanism that compresses a compressible fluid using the output of a drive source such as an electric motor, and is a mechanism generally referred to as a compressor. Such mechanisms include various types such as a swash plate type, a vane type, and a screw type.
In this specification, unless otherwise specified, the compressor means an assembly of an electric motor and a compression mechanism.

As a swash plate type compressor, for example, as described in JP-A-2004-44500, an electric motor housed in a housing, a swash plate rotated by the electric motor, and a reciprocating motion by rotation of the swash plate And a piston (compression mechanism). In the swash plate compressor, the swash plate is rotated by an electric motor, a compression mechanism including a piston and the like is driven by the rotation of the swash plate, and the compressive fluid is compressed by the reciprocating motion of the piston.
As described in, for example, Japanese Patent Application Laid-Open No. 2003-148332, a wobble compressor includes a drive plate that is connected to a main shaft, rotates, and swings when tilted, and a drive plate via a thrust bearing. A compression mechanism including a wobble plate attached to the connecting rod and a connecting rod connecting the wobble plate and the piston is driven by an electric motor. In the wobble compressor, the compressible fluid is compressed by reciprocating the piston by swinging the wobble plate accompanying the rotation of the drive plate.
Japanese Unexamined Patent Publication No. 2004-44500 (page 6-14, FIG. 2) JP 2003-148332 A (page 3-6, FIG. 1)

However, since the conventional swash plate compressor and wobble compressor as described above are provided with a compression mechanism on the output side of the electric motor (the side on which the output shaft protrudes), the shaft of the compressor inevitably. There has been a problem that the length in the center direction (direction in which the axis of the compressor extends) becomes long. That is, in such a compressor, it is necessary to arrange the electric motor and the compression mechanism side by side in the direction in which the axis of the drive shaft of the electric motor extends (appropriately described as “serially arranged”). In view of the demand for realizing the functions and abilities required of the drive source and the compression mechanism, there is a limit to shortening the length in the above direction (referred to as “shortening” as appropriate).
For example, in a swash plate compressor, an electric motor and a compression mechanism composed of a swash plate and a piston are arranged in series, and the functions (output, discharge capacity, etc.) required for each are realized. Since there is a limit to shortening the length of each component, the axial dimension of the compressor is significantly longer than the axial dimension of the compression mechanism alone. The length of the shaft center direction is longer than that when only the compression mechanism is used.
In the wobble compressor, an electric motor and a compression mechanism composed of a wobble plate, a drive plate, a piston, and the like are arranged in series, and the axial length of the compressor is inevitable.

  An object of the present invention is to provide a compressor having a novel structure in which the serial arrangement of the electric motor and the compression mechanism is eliminated.

  In order to achieve the above object, the present invention is connected to an electric motor that rotates a drive shaft, a conversion mechanism that converts a rotational movement of the drive shaft into a reciprocating motion in a substantially linear direction, and the conversion mechanism, It is provided outside the electric motor with respect to the drive shaft so as to surround the electric motor, reciprocates in conjunction with the reciprocating motion by the conversion mechanism, sucks compressive fluid from an external circuit, compresses it, And a compression mechanism having a piston for discharging the compressed fluid to an external circuit. Each component is housed in one housing.

In the compressor, it is preferable that the compression mechanism includes at least a compression chamber and the piston, and the compression chamber is formed in the housing.
Furthermore, the central axis of the compression chamber may be substantially parallel to the axis of the drive shaft. This can be said that the center axis of the cylinder bore is substantially parallel to the axis.
The housing is composed of at least two housings, and the first housing covers the electric motor, the compression chamber / cylinder bore, and a port for sucking compressive fluid from the external circuit, A passage that connects the port and the compression chamber / cylinder bore, and a valve that communicates the port with the compression chamber / cylinder bore when the compression mechanism is in the suction process. A port provided on the side opposite to the side where the conversion mechanism is provided with respect to the electric motor, a discharge chamber is formed at a position facing the compression chamber / cylinder bore, and the discharge chamber and an external circuit are connected to each other Preferably, the compression chamber / cylinder bore and the discharge chamber are communicated with each other, and a valve is provided for communicating between the compression mechanism and the discharge chamber when the compression mechanism is in the discharge process. There.
The first casing and the second casing are connected by a bolt at least on a straight line substantially the same as the axis of the drive shaft, and at least the drive shaft is lubricated by using the screw groove for the bolt. A lubricating oil supply mechanism that supplies oil may be provided.
The conversion mechanism may be either a wobble type conversion mechanism or a swash plate type conversion mechanism.
There may be further provided an urging member that applies a force in a direction that substantially coincides with the axis of the drive shaft and that moves away from the electric motor.
In addition, among the members that are provided around the electric motor and move relatively with respect to the housing, a member that is substantially affected by the magnetic force from the motor when moving is made of a magnetic material. A magnetic material may be used.
The urging member may be a nonmagnetic material.

  ADVANTAGE OF THE INVENTION According to this invention, the compressor of the novel structure from which the serial arrangement | positioning of an electric motor and a compression mechanism was eliminated can be provided.

(First embodiment)
Hereinafter, a compressor according to a first embodiment will be described with reference to FIGS.
In the compressor according to this embodiment, an electric motor 18 and a wobble compression mechanism 10 (an assembly of a wobble conversion mechanism 28 and a compression mechanism 10) are accommodated in a housing 11, and the electric motor 18 is It is a drive source for the compression mechanism 10.
In other words, the wobble type compression mechanism 10 is provided on the electric motor 18 on the radial direction side of the drive shaft 21 (perpendicular direction with respect to the axis of the drive shaft 21), and the housing 11 is provided on the outer side. It has been. The wobble conversion mechanism 28 is provided on the output side of the electric motor 18 (on the axial direction side of the drive shaft 21).
That is, the electric motor 18 and the wobble compression mechanism 10 are housed in one (or a set) of housings 11, and the electric motor 18 and the wobble compression mechanism 10 are arranged in series. Not.
In the present embodiment, the compressor is used in a refrigeration apparatus that compresses the compressive fluid flowing in from the refrigerant circuit C as an external circuit and returns the compressed fluid to the refrigerant circuit C. Where appropriate, it is referred to as “refrigerant”). For example, the compressive fluid may use a chlorofluorocarbon refrigerant, and is not intended to limit the type of compressive fluid.
The refrigerant circuit C includes at least an oil separator 48.

[About housing]
The housing 11 includes a first housing body 12, a second housing body 13, and a third housing body 14 as a housing. However, the housing 11 has at least two housings (the first housing body 12 and the second housing body 13 and the fourth housing body 14; that is, the former housing can be divided even if it is an integral structure. May also be configured.
The second housing body 13 is joined to one end of the first housing body 12.
The third housing body 14 is joined to the other end of the first housing body 12.
That is, the housing 11 is one (a set) of housings constituted by the first housing body 12, the second housing body 13, and the third housing body 14.
A gasket 15 is preferably interposed between the first housing body 12 and the second housing body 13 in order to maintain airtightness.
As shown in FIG. 3, a valve plate 40 is interposed between the first housing body 12 and the third housing body 14. The valve plate 40 has a discharge passage 40a that communicates from one chamber to the other chamber.
Each housing body may be arranged as described above and joined by any method capable of exhibiting performance such as strength required for the housing 11.
In the present embodiment, the housing bodies are joined as follows.
The first housing body 12 and the second housing body 13 are joined using a joining bolt (not shown).
The first housing 12 body and the third housing body 14 are joined using a joining bolt 16 near the outer periphery of the third housing body 14 and a joining bolt 17 near the center.
In the present embodiment, as appropriate, the center of each housing body substantially coincides with the center in the radial direction of the drive shaft 21 (the axis of the drive shaft), and the outer periphery of each housing body is the outer side of the drive shaft 21 in the radial direction. It is written that it exists.

The first housing body 12 has a cylindrical body portion 12a and a lid portion 12b that covers an end portion of the body portion 12a, and preferably both are integrally formed.
Therefore, it has a substantially bottomed cylindrical shape with the lid portion 12b as a bottom and the body portion 12a as a side surface.
An electric motor 18 is accommodated in the trunk portion 12a.
In addition to the cylinder bore 39, the lid portion 12b is formed with a bolt hole 12c for holding the joining bolt 16 for joining the third housing body 14 and the first housing body 12, as shown in FIG. Is done.
Also, a bolt hole 12 d for holding a joining bolt 17 for joining the third housing body 14 and the first housing body 12 may be formed at the center of the lid portion 12 b of the first housing 12.
Even when a refrigerant that becomes high pressure after compression is used by actively joining the centers of both 12 and 14 using the joining bolt 17, the drive motor for the lid 12 b that receives the pressure of the refrigerant after discharge. The bending to the 18 side can be prevented, and the bonding bolt 17 acts more effectively for maintaining the bonding as the refrigerant to be handled becomes higher in pressure.
The second housing body 13 forms a conversion mechanism accommodation chamber 27 together with the first housing body 12.

The third housing body 14 includes a discharge chamber 14a and a discharge port 47 as a port connecting the discharge chamber 14a and the refrigerant circuit C.
It has.
The third housing body 14 has a bolt hole 14 c for the joining bolt 16 and a bolt hole 14 d for the joining bolt 17.
A discharge valve forming plate 46 is interposed between the valve plate 40 and the third housing body 14.
The discharge valve forming plate 46 includes a discharge valve 46a corresponding to the discharge passage 40a.
The discharge valve 46a is a lead type check valve that can be bent.
The discharge valve 46a closes the discharge passage 40a when the low-pressure refrigerant is sucked into the compression chamber 41, and opens the discharge passage 40a when the compressed high-pressure refrigerant is discharged.
The third housing body 14 has a lubricating oil passage 14e formed so as to connect the bolt through hole 14d to the outside.
The lubricating oil passage 14 e and the oil separator 48 are connected by a lubricating oil supply pipe 49.
The oil separator 48 separates and collects the lubricating oil in the high-pressure refrigerant discharged from the discharge chamber 14a. The lubricating oil supply pipe 49 and the lubricating oil passage 14e supply lubricating oil from the oil separator 48 to the bolt through hole 14d.
That is, the lubricating oil supply pipe 49 and the lubricating oil passage 14e correspond to a lubricating oil supply path as a lubricating oil supply mechanism that supplies the lubricating oil to the bolt through hole 14d.
The screw groove of the bolt hole 12d and the screw groove of the joining bolt 17 serve as a throttle for the lubricating oil supplied at a high pressure, and the appropriate lubricating oil can be supplied to the thrust bearing 26 in the second shaft support portion 23.
The lubricating oil supply path has the lubricating oil supply pipe 49, the lubricating oil passage 14e, the bolt through hole 14d, and the first bolt hole 12d. For example, the lubricating oil passage may be connected to the bolt hole 12d. Any configuration and means other than the bolt hole 12d may be used as long as the lubricating oil supply path includes the bolt hole 12d communicating with at least the second shaft support portion 23.

[Conversion room]
The conversion mechanism accommodation chamber 27 is formed between the electric motor 18 and the second housing body 13 by the first housing body 12 and the second housing body 13. The conversion mechanism accommodation chamber 27 accommodates a conversion mechanism 28 that converts the rotational movement of the drive shaft 21 into the reciprocating motion of the piston 42.
In this embodiment, the conversion mechanism accommodation chamber 27 corresponds to a refrigerant suction chamber. Specifically, the first housing body is provided with a suction port 29 as a port for sucking in refrigerant that has been consumed in the refrigerant circuit C and has become low pressure. That is, in the compressor according to the present embodiment, the space (that is, the suction chamber) into which the low-pressure refrigerant is introduced from the refrigerant circuit C is the conversion mechanism accommodation chamber 27.

The thickness of the body 12 a of the first housing body 12 varies depending on the position of the drive shaft 21 in the axial direction.
Specifically, the thickness at the position where the stator 19 is accommodated is thicker than the thickness at the position where the conversion mechanism accommodation chamber 27 is provided.
This is because the communication passage 38 and the cylinder bore 39 constituting the compression mechanism 10 are formed in the body portion 12a at the position where the electric motor 18 is accommodated.

[Cylinder bore]
As shown in FIG. 2, the compressor according to this embodiment has nine cylinder bores 39 formed therein.
Naturally, nine communication passages 38 are formed. However, this number is not limited.

Here, in the communication passage 38 and the cylinder bore 39, a space closest to the inner peripheral surface via the first housing body 12, such as a space outside the compressor, a space in which the electric motor 18 is accommodated, and other cylinder bores. The closest position (short distance) among the inner walls such as 39 is referred to as a “second thickness”. The second thickness is set such that the cylinder bore 39 is thicker than the communication passage 38. This is because the pressure generated in the cylinder bore 39 is higher than that in the communication passage 38.
Specifically, in the compressor shown in FIG. 1, the first housing body 12 has a communication path 38 formed from the conversion mechanism accommodation chamber 27 side to the other end, and a cylinder bore 39 is formed on the end side. Is formed. The cylinder bore 39 passes through the end portion.

  The inner peripheral surface of the communication path 38 (the surface that coincides with the side surface of the substantially cylindrical portion constituted by the first housing body 12) can be manufactured with lower accuracy than the inner peripheral surface of the cylinder bore 39. This is because the cylinder bore 39 is required to be manufactured with high processing accuracy because of its function to approximately match the outer diameter of the piston 42, but there is no requirement for the communication path 38.

In the compressor shown in FIG. 1, by appropriately setting the thickness of the body 12a (including the second thickness in this paragraph), functions required for the compression mechanism 10, such as the strength of the housing against pressure, etc. However, it is naturally possible to realize the above function by other factors or by combining other factors. For example, depending on the position of the first housing body 12, the material is changed, the processing method (forging method or casting method) is changed, the layer structure is made of the same or different material, and the layer structure is different or one layer. May be provided. In addition, the portions having different structures may be separately manufactured and combined by using a known housing connecting method.
In addition, the first housing body 12 includes the body portion 12a and the lid portion 12b which are integrally formed. However, the first housing body 12 need not be integrally formed.

  A region covered with the valve plate 40 and the cylinder bore 39 is a compression chamber 41. A discharge passage 40a in the valve plate 40 communicates the compression chamber 41 and the discharge chamber 14a. Further, a gasket 52 is preferably interposed between the valve plate 40 and the first housing body 21 in order to keep the compression chamber 41 airtight.

[Piston]
A piston 42 is provided in the cylinder bore 39, and the piston 42 is connected to the wobble plate 32 via a rod 43.
The piston 42 is formed with a connecting portion 42 a for connecting to the rod 43.
The rod 43 is connected to a connection portion 32 b provided on the wobble plate 32.
Further, the rod 43 is configured such that its axis coincides with a straight line substantially parallel to the axis of the drive shaft 21 so that the reciprocating power input from the wobble plate 32 becomes reciprocating power in a direction substantially coincident with the straight line. Is done.

The piston 42 is a suction passage that connects the front and rear in the axial direction of the cylinder bore 39, that is, the side facing the valve plate 40 (head 42c) and the side contacting the rod 43 (side where the connecting portion 42a is provided, bottom 42d). 42b is formed.
That is, the suction passage 42 b communicates the communication passage 38 and the compression chamber 41.
Therefore, the refrigerant sucked into the conversion mechanism accommodation chamber 28 from the suction port 29 is sucked into the compression chamber 41 through the communication passage 38 and the suction passage 42b in order.
Here, the suction passage 42b is a pair of upper and lower through holes. However, the through hole of the suction passage 42b may be a single passage having an annular cross section, and the number and shape of the suction passages 42b are not particularly limited.

The piston 42 is provided with a mechanism for opening and closing the suction passage 42b at the head portion 42c. In the present embodiment, this mechanism includes a suction valve 44 and a restriction bolt 45.
The restriction bolt 45 is provided as a member for restricting the distance that can be separated from the head portion 42c of the suction valve 42 at the center portion of the head portion 42c of the piston 42 (the portion where the suction passage 42b is not provided). Entered).
The restriction bolt 45 has a head portion 45b and a shaft portion 45a. As described above, the shaft portion 45 a has a head portion 42 c (side on which the bottom portion 42 b is not provided) connected to the piston 42 or inserted into the piston 42.
A ring-shaped intake valve 44 is disposed in a portion exposed to the outside of the piston 42 so as to surround the periphery thereof.
The suction valve 44 surrounds the shaft portion 45a, is movable in the axial direction of the shaft portion 45a, and has an inner diameter smaller than the outer diameter of the shaft portion 45a so that the movement is stopped by the head 45b. Is set to be narrower than the outer diameter of the head 45b.
Since the pressure in the compression chamber 41 becomes higher than the pressure in the conversion mechanism housing chamber 27 in the compression stroke, the suction valve 44 is pressed against the head portion 42c of the piston 42 to block the suction passage 42b. Since this is the reverse of the above, the suction passage 42b is released.
In order to reduce the dead volume, it is preferable that the head 45b of the regulating bolt 45 enters the discharge passage 40a when the piston 42 is closest to the valve plate 40 (see the two-dot chain line in FIG. 3). ).

[Electric motor]
The electric motor 18 is a motor that rotates the drive shaft 21 and outputs it in any one of the axial directions of the drive shaft 21. In the present embodiment, the electric motor 18 includes a stator 19 and a rotor 20. Rotate.
The stator 19 is supported by the trunk portion 12a.
The rotor 20 has a drive shaft 21 fixed inside thereof.
One end of the drive shaft 21 is pivotally supported by a first pivotal support 22 provided in the second housing body 13, and the other end is pivotally supported by a second pivotal support 23 provided in the lid 12b. ing.
Both shaft support portions 22 and 23 are provided with radial bearings 24 and 25, and the second shaft support portion 23 is further provided with a thrust bearing 26, which is in contact with the shaft end of the drive shaft 21.
The electric motor 18 is fixed in the housing 11 as described above.

[Conversion mechanism]
The conversion mechanism 28 converts the rotational movement of the drive shaft 21, which is an output from the electric motor 18, into a reciprocating movement (movement reciprocating on a substantially straight line) of the piston 42 for compressing the compressive fluid in the compression mechanism 10. Mechanism.
In the present embodiment, a mechanism is adopted in which a piston 42 provided on the electric motor 18 side is reciprocated with respect to the conversion mechanism 10 as a mechanism used in the wobble type compressor.
That is, in the conversion mechanism used in the conventional wobble type compressor, the direction in which the rotational motion is converted and output as the reciprocating motion is opposite to the conventional direction, that is, in a straight line parallel to the axis of the drive shaft 21. This is a mechanism in which the electric motor 18 is provided.
Hereinafter, the conversion mechanism 28 according to the present embodiment will be described in detail.

[About lug plate]
The conversion mechanism 28 includes a lug plate 30, a universal joint 31, and a wobble plate 32.
The lug plate 30 includes a shaft fitting portion 30a having a shaft hole, and a plate portion 30b formed around the shaft fitting portion 30a (outside the shaft fitting portion 30a with respect to the central axis of the shaft hole). Have The shaft fitting portion 30a is spline-coupled to one shaft end of the drive shaft 21 or the vicinity of the shaft end in the shaft hole.
That is, the shaft fitting portion 30a and the substantially shaft end on the second housing 13 side of the drive shaft 21 are spline-fitted with each other.
As described above, since the drive shaft 21 and the lug plate 30 are spline-coupled, the lug plate 30 can slide with respect to the axial direction of the drive shaft 21.
If such a configuration is adopted, it is easier to assemble and remove the conversion mechanism 28 on the second housing body 13 side during assembly work and maintenance work of the compressor 10 than when such a configuration is not adopted. It becomes. However, it is not essential that the drive shaft 21 and the lug plate 30 are spline-fitted as described above.

The plate portion 30 b includes an inclined surface 30 c that faces the electric motor 18 side and is inclined with respect to the axis of the drive shaft 21, with the axis as the approximate center.
The plate portion 30 b includes a vertical surface 30 d that is perpendicular to the axis of the drive shaft 21 and is centered on the axis on the second housing body 12 side. The vertical surface 30 d faces the second housing 13 with the thrust bearing 33 interposed therebetween.
Therefore, the portion of the second housing 13 that contacts the thrust bearing 33 includes an inner wall surface 13 a that is perpendicular to the axis of the drive shaft 21. In other words, the vertical surface 30d and the inner wall surface 13a face each other with the thrust bearing 33 interposed therebetween.
The thrust bearing 33 reduces the friction generated between the lug plate 30 and the second housing body 13 when the lug plate 30 rotates. The thrust bearing 33 provided in the vicinity of the outer periphery of the lug plate 30 has a function of preventing the lug plate 32 from tilting around the axis of the drive shaft 21.
That is, even if the lug plate 30 receives a force biased from the wobble plate 32 side, the lug plate 30 is supported by the thrust bearing 33 without being inclined.
The lug plate 30 is joined to the drive shaft 21 via the shaft fitting portion 30a so that the center of the inclined surface 30c and the vertical surface 30d and the shaft center of the drive shaft 21 are substantially coincident with each other.
For this reason, when the drive shaft 21 rotates, it rotates synchronously with the drive shaft 21 around the axis.
In this embodiment, the shaft fitting portion 30a is made of an iron-based material, and the plate portion 30b is made of an aluminum-based material.
If the shaft fitting portion 30a is made of an iron-based material, the shaft fitting portion 30a can easily secure the strength corresponding to the torque of the drive shaft 21 as compared with the case where such a material is not adopted. .
If the plate portion 30b is made of an aluminum-based material, the weight of the plate portion 30b can be reduced. Compared to the case where such a material is not used, the plate portion 30b has a lug plate 30 that accompanies the rotation of the drive shaft 21. It is easy to reduce the inertial force.
However, it is not essential to specify the materials of the shaft fitting portion 30a and the plate portion 30b as described above.

[About universal joints]
The universal joint 31 is provided closer to the electric motor 18 than the inclined surface 30 c of the lug plate 30 and closer to the lug plate 30 than the electric motor 18, and covers the drive shaft 21.
The universal joint 31 has a function of inclining the wobble plate 32 with respect to the axis of the drive shaft 21 and a function of preventing co-rotation with the drive shaft 21 of the wobble plate 32.
That is, the universal joint 31 is prevented from rotating even when the drive shaft 21 rotates.
The universal joint 31 includes a bearing member 34 and a joint member 36.

As shown in FIG. 4, the bearing member 34 includes a communication hole, a bearing 35, a connecting piece 34a, a pin hole 34b, and an extending portion 34c.
The bearing member 34 functions to support the drive shaft 21, to rotate the wobble plate 32 with respect to the axis of the drive shaft 21 (angle range of rotation about the axis), and to rotate the drive shaft 21. Along with this, the wobble plate 32 is prevented from rotating together.
The bearing member 34 communicates with and supports the drive shaft 21.
That is, a communication hole is formed at a position where the drive shaft 21 is inserted, and a bearing 35 is attached to the communication hole. In other words, the bearing member 34 supports the drive shaft 21 via the communication hole and the bearing 35.
The bearing member 34 has a connecting piece 34a extending from the periphery of the communication hole to the wobble plate 32 side.
In this embodiment, it is a pair of upper and lower connecting pieces 34a with the drive shaft 21 positioned therebetween.
Each connecting piece 34 a is provided with two pin holes 34 b on a straight line that is substantially perpendicular to the axis of the drive shaft 21. That is, the central axes of the pin holes 34b substantially coincide with each other (being substantially coaxial).

  The bearing member 34 includes at least one extending portion 34 c that extends to the first housing body 12. The extending part 34c is formed with at least one through hole 34d on the first housing body 12 side. An anti-rotation bolt 37 is inserted into the through hole 34 b, and the extending portion 34 c is fixed to the first housing body 12. Therefore, even if the drive shaft 21 rotates, it does not rotate by this rotational force. Of course, other known methods may be used to prevent the bearing member 34 from rotating around the drive shaft 21 (rotating in synchronization with the drive shaft 21 or rotating).

The joint member 36 is a substantially cross-shaped member 36 connected to the bearing member 34 and the wobble plate 32. In other words, the joint member 36 can also be referred to as a member that connects the bearing member 34 and the wobble plate 32.
The main body of the joint member 36 is disposed so as to cover the drive shaft 21, and the outer periphery of the main body is in contact with the communication piece 34 a. That is, the main body has a substantially ring shape, and the inner surface thereof is disposed so as to face the outer peripheral surface of the drive shaft 21, and the outer surface thereof is disposed so as to face the surface (inner peripheral surface) of the communication piece 34a on the drive shaft 21 side. .
The joint member 36 has a pair of connecting pins 36a each having a shaft center whose straight line perpendicular to the shaft center of the drive shaft 21 substantially coincides with the outer periphery of the joint member 36, preferably with the body of the joint member 36. It is formed and provided.
Each connecting pin 36a has an outer portion (a portion opposite to the outer peripheral surface side of the joint member 36 / a portion protruding further outside the outer peripheral surface of the joint member 36) accommodated in the pin hole 34b of the bearing member 34. Yes.
Therefore, the joint member 36 is disposed at the above-described position by accommodating the connecting pin 36a in the pin hole 34b.
Further, the joint member 36 can rotate with respect to the bearing member 34 with the connecting pin 36a as an axis. That is, since it becomes possible to move around a straight line (straight line substantially coincident with the axis) perpendicular to the axis of the drive shaft 21, a relative position other than the axis relative to the bearing member 34 (for example, the joint member 36). It is possible to change the position of the outer peripheral surface.
In order to enable such an operation, the inner peripheral surface of the joint member 36 main body and the drive shaft 21 are moved within a rotation range required for the joint member 36 (an angular range rotating with respect to the axis). The diameter of the inner peripheral surface and the diameter of the drive shaft 21 are set so as to be possible.
That is, a sufficient gap is provided between the two.
In the present embodiment, in order to shorten the distance (compressor radius / compressor width) from the axis of the drive shaft 21 as a reference, the drive shaft 21 is at least at a position corresponding to the joint portion 36. The diameter is thinner than other parts (in this embodiment, the diameter of the joint portion 36 is smaller than the diameter of the electric motor 18 as shown in FIG. 1).
The connecting pin 36b is located on the outer peripheral surface of the joint member 36 main body at a position where the connecting pin 36a is not provided, preferably a straight line perpendicular to the axis of the connecting pin 36a and perpendicular to the axis of the drive shaft 21. It is provided at a substantially coincident position. The connecting pin 36 b is a member for connecting the wobble plate 32 and the joint member 36.

In this embodiment, as shown in FIG. 1, a coil spring 50 as an urging member is fitted on the drive shaft 21 between the bearing member 34 and the rotor 20.
A thrust bearing 51 is interposed between the coil spring 50 and the bearing member.
The biasing force acting on the rotor 20 of the coil spring 50 causes the other end of the drive shaft 21 to abut against the thrust bearing 26.
The rotor 20 can maintain an appropriate position with respect to the stator 19 by this biasing force.
That is, the coil spring 50 adjusts the position of the rotor 20 in the axial direction of the drive shaft 21.
The biasing force acting on the bearing member 34 of the coil spring 50 presses the conversion mechanism 28 against the second housing body 13.
In other words, the urging member applies a force in a direction in which the conversion mechanism 28 substantially coincides with the axis of the drive shaft 21 and away from the electric motor 21.
Thereby, the piston 42 is easily maintained at an appropriate position with respect to the second housing body 13.
That is, the position of the piston 42 set with the second housing body 13 as a reference is more than the design tolerance in the axial direction of the drive shaft 21 generated in each part than the position of the piston 42 set with the first housing body 12 as a reference. It is easy to suppress the influence of.
This absorbs the accumulated tolerance of each part in adjusting the piston top clearance (the distance between the piston head 42c and the valve plate 40).

[About wobble plate]
The wobble plate 32 is provided between the lug plate 30 and the universal joint 31 and is connected to the universal joint 31.
The wobble plate 32 is a ring-shaped plate that is substantially centered on the axis of the drive shaft 21, and an opening hole 32 a through which the drive shaft 21 passes is formed at the center.
A connecting piece 32b having a pin hole 32c protrudes from the drive motor 18 side. The pin hole 32c is connected to the joint member 36 by inserting the connecting pin 36b.
The pin hole 32c is configured such that the connecting pin 36b can relatively rotate inside thereof.
In the present embodiment, the connecting pin 36b can be rotated relative to the pin hole 32c by appropriately setting the size of each diameter.
Since such a configuration is adopted, the wobble plate 32 can be connected to the joint member 36 and can be rotated about the connecting pin 36b which is a component of the joint member 36 as an axis.
The rotation of the joint member 36 around the axis of the connecting pin 36a and the rotation of the wobble plate 32 around the axis of the connecting pin 36b cause the inclination of the wobble plate 32 with respect to the drive shaft 21 to move around the entire circumference of the drive shaft 21. Is possible.
That is, the wobble plate 32 can be inclined on the entire peripheral surface of the drive shaft 21 by combining the rotations of the both 36 and 32. Since the wobble plate 32 is connected to the universal joint 31 that is prevented from rotating and the wobble plate 32 and the drive shaft 21 are not connected, the wobble plate 32 does not rotate synchronously with the drive shaft 21.

The wobble plate 32 is in contact with the lug plate 30 via a thrust bearing 53 on the side facing the lug plate 30.
The abutment through the thrust bearing 53 in this way is that when the drive shaft 21 rotates, the lug plate 30 rotates with the rotation, but the wobble plate 32 does not rotate, so the friction between the two is reduced. This is to prevent the rotation of the wobble plate 32 from being hindered. Therefore, as long as it is a mechanism which implement | achieves such a function, it is also possible to employ | adopt other well-known mechanisms.
The wobble plate 32 has a connection portion 32d connected to the rod 43 on the electric motor 18 side and in the vicinity of the outer periphery (the electric motor 18 side in the vicinity of the outer periphery).

Thus, the compressor according to the present embodiment is provided with the compression mechanism 10 outside the electric motor 18. More specifically, the following mechanism is provided to realize refrigerant compression.
1) A conversion mechanism 28 is provided on the output side of the electric motor 18.
2) The rotational force generated by the electric motor 18 is converted into reciprocating power in a direction substantially parallel to the axis of the drive shaft 21 by the conversion mechanism 28.
The reciprocating power means a force that reciprocates substantially linearly.
3) The reciprocating power is transmitted to the compression mechanism 10 provided outside the electric motor 18.
That is, the piston 42 reciprocates, and refrigerant suction / compression / discharge is realized.
In other words, the conversion mechanism 28 converts the rotational force input from the electric motor 18 on the opposite side to the output side (the conversion mechanism 28 side and its direction with respect to the power motor 18 with respect to a plane parallel to the drive axis). Output as reciprocating power.
This force is input to the compression mechanism 10 provided outside the electric motor 18 (position far from the position where the electric motor 18 is present with respect to the axis of the drive shaft). And it is transmitted to the compression mechanism 10 which compresses a refrigerant | coolant by reciprocating motion, such as piston movement, in detail. The compression mechanism 10 compresses the refrigerant by the input force (reciprocating power).
Thus, in the compressor according to the present embodiment, the compression mechanism 10 is provided in the housing of the power motor 18. In other words, the power motor 18 is provided inside the compression mechanism 10.
A member that is provided around the electric motor 18 and moves relatively with respect to the housing 11, for example, a conversion mechanism 28 or the like, which is made of a magnetic material, the movement of the electric motor 18 influences the magnetic force from the electric motor 18. The substantially receiving member may be a nonmagnetic material.

Next, the driving operation of the compressor 10 according to this embodiment will be described.
When a current is supplied to the electric motor 18, the drive shaft 21 is rotated along with the rotation of the rotor 20.
The lug plate 30 is rotated along with the rotation of the drive shaft 21, and the rotation of the lug plate 30 continues because the wobble plate 32 corresponds to the inclined surface 30 c of the rotating lug plate 30 as the lug plate 30 rotates. As a result, the inclination angle of the wobble plate 32 changes.
As the inclination angle of the wobble plate 32 changes, the outer periphery of the wobble plate 32 swings and the rod 43 reciprocates.
As the rod 43 reciprocates, the piston 42 reciprocates in a substantially linear direction within the compression chamber 41.
As described above, the rotational movement of the drive shaft 21 is converted into the substantially linear reciprocation of the piston 42 by the conversion mechanism 28.

In the suction process of the piston 42 from the top dead center to the bottom dead center, the low-pressure refrigerant sucked into the conversion mechanism housing chamber 27 from the suction port 29 passes through the communication passage 38 and passes through the suction passage 42b of the piston 42 to the compression chamber. 41 is inhaled.
In this suction process, the suction valve 44 of the piston 42 is opened due to the pressure difference between the compression chamber 41 and the communication passage 38 that becomes low pressure as the piston 42 moves to the bottom dead center.
Next, in the discharge process of the piston 42 from the bottom dead center to the top dead center, the pressure in the compression chamber 41 increases as the piston 42 moves to the top dead center, and the difference between the high-pressure compression chamber 41 and the communication passage 38 is increased. The suction valve 44 is closed by the pressure.
When the piston 42 reaches near the top dead center, the pressure in the compression chamber 41 becomes high, so that the discharge valve 46a bends, opens the discharge passage 40a, and high-pressure refrigerant is discharged to the discharge chamber 14a through the discharge passage 40a. .

The high-pressure refrigerant discharged into the discharge chamber 14a is sent to the refrigerant circuit C through the discharge port 47, and the lubricating oil contained in the high-pressure refrigerant is separated and recovered by the oil separator 48 included in the refrigerant circuit C.
A part of this lubricating oil is supplied to the bolt through hole 14 d of the third housing body 14 through the lubricating oil supply pipe 49 by utilizing the high pressure of the refrigerant in the oil separator 48.
The lubricating oil is supplied to the thrust bearing 26 in the second shaft support portion 23 through the bolt through hole 14d into which the joining bolt 17 is inserted and the bolt hole 12d into which the joining bolt 14d is screwed.
By supplying the lubricating oil to the thrust bearing 26, the lubricating oil is supplied to the radial bearing 25 in the vicinity of the thrust bearing 26.
The first housing 12 is filled with a low-pressure refrigerant before compression, and the lubricating oil supplied to the bolt through hole 14d is lubricating oil contained in the high-pressure refrigerant after compression. Although the lubricating oil is guided to the second shaft support portion 23, the screw groove of the joining bolt 17 and the screw groove of the bolt hole 12d serve as a throttle, and a sudden supply of the lubricating oil is avoided.

The compressor 10 according to this embodiment has the following effects.
(1) The electric motor 18 that rotates the drive shaft 21, the conversion mechanism 28 that converts the rotational movement of the drive shaft 21 into a reciprocating motion in a substantially linear direction, and the conversion mechanism 28 are connected to the drive shaft 21. Is provided outside the electric motor 18 so as to surround the electric motor 18, and reciprocates in conjunction with the reciprocation by the conversion mechanism 28 to suck in compressible fluid from an external circuit and compress it. And a compression mechanism 10 having a piston 42 for discharging the compressed fluid to an external circuit, and each component is housed in one housing 11. Such a configuration can provide a compressor having a novel structure that has not been conventionally available. This is preferable in that the serial arrangement of the electric motor 18 and the compression mechanism 10 is eliminated.
(2) Since the compression mechanism 10 includes at least the compression chamber 41 and the piston 42, and the compression chamber 41 is formed in the housing 11, it is preferable in terms of downsizing the compressor.
(3) The central axis of the compression chamber 41 / cylinder bore 39 is substantially parallel to the axis of the drive shaft 21. Such a configuration is preferable in terms of efficient conversion when converting the rotational movement of the drive shaft 21 into the reciprocating movement of the piston 42.
(4) The housing 11 is composed of at least two housings. The first housing covers the electric motor 18 and sucks compressive fluid from the compression chamber 41 / cylinder bore 39 and the external circuit. A port that connects the port to the compression chamber 41 / cylinder bore 39, and a valve that communicates the port with the compression chamber 41 / cylinder bore 39 when the compression mechanism 10 is in the suction process. The second casing is provided on the side opposite to the side on which the conversion mechanism 28 is provided with respect to the electric motor 18, and the discharge chamber 14a is located at a position facing the compression chamber 41 / cylinder bore 39. And a port for connecting the discharge chamber 14a and an external circuit is provided, the compression chamber 41 / cylinder bore 39 and the discharge chamber communicate with each other, and the pressure Mechanism valve for communicating therebetween is provided when in the discharge process. Such a configuration is preferable in that the space corresponding to the suction chamber is separated from the discharge chamber. Furthermore, the compressible fluid in the suction chamber hardly receives heat from the discharge chamber.
(5) The first housing and the second housing are connected by a bolt 17 on at least a straight line substantially the same as the axis of the drive shaft 21, and a screw groove for the bolt 17 is used. A lubricating oil supply mechanism for supplying lubricating oil to at least the drive shaft 21 is provided. Such a configuration is preferable in that the vicinity of the shaft end of the drive shaft 21 is lubricated.
(6) The conversion mechanism 28 is a wobble type conversion mechanism. Such a configuration is preferable in that the rotational movement of the drive shaft 21 is converted into the reciprocating movement of the piston 42.
(7) An urging member that applies a force in a direction that substantially matches the axis of the drive shaft 21 and away from the electric motor 18 is further provided. Such a configuration is preferable in that it easily absorbs the tolerance of each element that tends to occur in the axial direction of the drive shaft 21.
(8) Among the members that are provided around the electric motor 18 and move relatively with respect to the housing 11, the movement substantially affects the magnetic force from the electric motor 18 when made of a magnetic material. Non-magnetic material is used for the members. Such a configuration is preferable in that it prevents magnetism from the electric motor to the member that moves relative to the housing 11. The force generated by the magnetism in the member can be prevented.
(9) The biasing member is a nonmagnetic material. Such a configuration is preferable in that the urging force of the urging member is kept substantially constant.

Further, it can be said that the following effects can be obtained. (10) The piston 42 reciprocating in the compression chamber 41, the electric motor 18 provided with the stator 19 and the rotor 20, and the drive shaft 21 that is rotationally driven by the electric motor 18. A conversion mechanism 28 that converts the rotational movement of the drive shaft 21 into a reciprocating motion of the piston 42, and a housing 11 that houses the electric motor 18 and the converting mechanism 28. A compressor 10 for sucking compressible fluid into the compression chamber 41 and discharging compressed high-pressure compressive fluid from the compression chamber 41, wherein the housing 11 is a first housing that supports at least the stator 19. A body 12, a second housing body 13 joined to one end of the first housing body 12, and a third housing joined to the other end. Includes a body 14, the compression chamber 41 is formed by the first housing member 12 and the cylinder bore 39 provided to the valve plate 40 to the first housing 12 which is interposed between the third housing member 14. For this reason, the compression chamber 41 is formed by the cylinder bore 39 provided in the first housing body 12 and the valve plate 40, whereby the electric motor 18 and the compression chamber 41 are arranged substantially in parallel, and the drive shaft 21 of the compressor 10 is arranged. The axial dimension can be made shorter than before.
(11) In the compressor 10, when the reciprocating direction of the piston 42 coincides with the axial direction of the drive shaft 21, the conversion mechanism 28 can easily convert the piston 42 into reciprocating motion. More preferred. Furthermore, it is also preferable in that the thickening of the thickness of the first housing body 12 can be suppressed.
(12) The conversion mechanism 28 is slid in the axial direction of the drive shaft 21 and is urged by an urging member interposed in the drive shaft 21 so as to be positioned between the rotor 20 and the conversion mechanism 28. 2 When the urging force is applied toward the housing body 13, the conversion mechanism is arranged with reference to the second housing body 13 by the urging force of the urging member to the second housing body 13, and is connected to the conversion mechanism 28. 42 is preferable in that it is disposed in the cylinder bore 39 in a state where the influence of design tolerances is suppressed. The rotor 20 faces an appropriate position with respect to the stator 19 by the biasing force of the biasing member to the third housing body 14.
(13) Further, when the biasing member in the compressor 10 is formed of a nonmagnetic material, the biasing of the biasing member by the electric motor 18 is prevented. This is preferable because there is no possibility of becoming unstable.

(14) The first housing body 12 is formed by a trunk portion 12a that supports the stator 19 and a lid portion 12b that closes an end portion of the trunk portion 12a on the third housing body 14 side, and the drive shaft 21 is A first shaft support portion 22 that penetrates the rotor 20 and supports the end of the drive shaft 21 on the conversion mechanism 28 side is formed in the second housing body 13, and the lid portion 12b is formed on the lid portion 12b. When the second shaft support portion 23 that pivotally supports the end portion of the drive shaft 21 that is directed toward the second shaft support portion 23 is provided, the lubricating oil is supplied to the second shaft support portion 23. It is more preferable in that it is supplied and the smooth rotation of the drive shaft 21 is maintained.
(15) Bolt holes 12d communicating with the second shaft support portion 23 are respectively formed in the first housing body 12 and the third housing body 14, and the lubricating oil supply path includes at least the bolt holes 12d. Lubricating oil contained in the compressible fluid in the discharge chamber 14a is supplied between the bolt 17 and the bolt hole 12d that are screwed into the bolt hole 12d, and is subjected to a throttling effect by the screw of the bolt 17 and the screw of the bolt hole. Is more preferable in that it is supplied to the second shaft support portion 23.

(16) In the compressor, the first housing body 12 and the second housing body 13 form a conversion mechanism accommodation chamber 27 in which the conversion mechanism 28 is accommodated, and the communication path that communicates the conversion mechanism accommodation chamber 27 and the cylinder bore 39. 38, a suction passage 42a provided in the piston 42 so as to communicate the communication passage 38 and the compression chamber 41, a suction valve 44 for opening and closing the suction passage 42a, a discharge chamber 14a formed in the third housing body 14, A discharge passage 40a communicating with the compression chamber 41 and the discharge chamber 14a and a discharge valve 46a for opening and closing the discharge passage 40a may be provided. In this way, the low-pressure compressible fluid before compression is sucked into the compression chamber 41 through the conversion mechanism accommodating chamber 27 or the communication passage 38 separated from the discharge chamber 14a, so that the high-pressure compression after compression in the discharge chamber 14a. There is little possibility of receiving heat from ionic fluid. Therefore, it is more preferable in that the reduction of the suction efficiency of the suction refrigerant due to the heat of the high-pressure compressive fluid can be suppressed. Furthermore, it is not necessary to provide a suction chamber in at least the third housing body 14, and the third housing body 14 can be simplified or reduced in weight, or even when the diameter of the cylinder bore is set small, This is more preferable in that the degree of freedom of design of the third housing body 14 is not significantly impaired.

(17) Any one of the conversion mechanisms 28 includes the lug plate 30 that has the inclined surface inclined with respect to the shaft center of the drive shaft 21 that is rotated with the drive shaft 21 while the drive shaft 21 is inserted; A universal joint 31 inserted through the drive shaft 21 and prevented from rotating with respect to the drive shaft 21, and connected to the universal joint 31, following the inclined surface of the lug plate 30, with respect to the axis of the drive shaft 21 And the rod 43 connecting the wobble plate 32 and the piston 42. When the lug plate 30 and the wobble plate 32 slide relative to the axial direction of the drive shaft 21, the drive shaft 21 The rotational motion is preferable in that it is converted into a reciprocating motion of the piston 42 via the rod 43 by the lug plate 30 and the wobble plate 32.
(18) The lug plate 30 includes a shaft fitting portion 30a fitted to the inserted drive shaft 21, and a plate portion 30b formed around the shaft fitting portion 30a. The shaft fitting portion 30a is made of iron. When the plate portion 30b is formed of a non-ferrous metal having a specific gravity smaller than that of the ferrous metal, the shaft fitting portion 30a has a sufficient strength so that the torque of the drive shaft 21 is applied to the lug plate 30. It is more preferable at the point which can be transmitted to. Further, the plate portion 30b formed around the shaft fitting portion 30a is preferably formed of a non-ferrous metal having a specific gravity smaller than that of the iron-based metal, so that the inertial force due to the rotation of the lug plate 30 is reduced. .
Incidentally, as the non-ferrous metal, an aluminum metal excellent in manufacturing cost and formability is suitable, but other titanium metals and the like may be used.

Next, another example of the piston will be described with reference to FIG.
Here, for convenience of explanation, some of the reference numerals are used in common with the above-described embodiment, and the above explanation is used for common points.
The piston 54 shown in FIG. 5 connects, in the cylinder bore 39, the piston portion 54a located on the valve plate 40 side, the sliding portion 54b located near the communication path 38, and the piston body 54a and the sliding portion 54b. Rod portion 54c.
That is, it can be said that the piston is supported by the first housing body 12 by the piston main body 54a and the sliding portion 54b.
For this reason, since the piston 54 has the piston main body 54 a and the sliding portion 54 b which are sufficiently separated from each other, the cylinder bore 39 is set to a length corresponding to the piston 54.
On the valve plate 40 side of the piston portion 54a, a restriction bolt 55, a suction valve 56, and a suction passage 54e are provided in the same manner as the piston 42 described above.
On the conversion mechanism side of the sliding portion 54b, a connection portion 54f for connecting the end portion of the rod 57 is formed.
The outer peripheral surface of the sliding portion 54a substantially coincides with the inner peripheral surface of the cylinder bore 39, and slides with respect to the inner peripheral surface.
The diameter of the rod portion 54c is set smaller than that of the piston main body 54a and the sliding portion 54b.
It is preferable to reduce the diameter of the rod portion 54c in order to reduce the weight of the piston, but it is not essential to reduce the diameter of the rod portion 54c. For example, the diameter of the rod portion 54c is made to substantially match the diameter of the piston main body 54a. It may be.
A part of the inner peripheral surface of the cylinder bore 39 is formed with a passage 39 a along the cylinder bore 39.
The passage 39a is a passage for allowing the refrigerant from the conversion mechanism accommodation chamber 27 to pass to the rod portion 54c side in the sliding portion 54b.
Even when the piston 54 is located at either the top dead center or the bottom dead center, the passage 39a may be a passage that allows the rod portion 54c side of the sliding portion 54c in the cylinder bore 39 and the conversion mechanism accommodation chamber 27 side to communicate with each other. . Here, the passage 39a is a concave groove along the cylinder bore 39. For example, the passage may be provided in the sliding portion 54b without providing the passage in the cylinder bore 39.
The piston 54 thus configured is longer than the piston 42 described above.
For this reason, the length of the rod 57 is shortened from the rod 43 by the length of the piston 54.
The lengthening of the piston 54 and the shortening of the rod 57 increase the durability against a force in a direction away from the axis of the rod 57, and prevent the possibility of buckling (breaking or bending) of the rod 57 during compression, for example.

(Second Embodiment)
Next, the compressor 60 according to the second embodiment will be described with reference to FIG.
A housing 61 of the compressor 60 shown in FIG. 4 is formed by a first housing body 62, a second housing body 63, and a third housing body 64.
An electric motor 68 having a stator 69 and a rotor 70 is accommodated in the first housing body 62.
The first housing 62 and the third housing 64 are joined by a joining bolt 66 near the outer periphery and a joining bolt 67 at the center.
Bolt holes 62 c are formed near the outer periphery of the first housing body 62.
A bolt through hole 64d corresponding to the bolt hole 62c is formed in the third housing 64.
At the center of the first housing body 62, a bolt hole 62 d communicating with the second shaft support portion 73 is formed.
The third housing body 64 has bolt through holes 64e corresponding to the bolt holes 62d.
The bolt through hole 64e of the third housing body 64 and the oil separator 98 are connected by a lubricating oil supply pipe 97, and the lubricating oil is supplied from the oil separator 98 to the bolt through hole 64e and the bolt hole 12d through the lubricating oil supply pipe 97. Supply.
That is, a lubricating oil passage as a lubricating oil supply mechanism is formed.
The screw of the bolt hole 62d and the screw of the joining bolt 67 serve as a throttle for the lubricating oil supplied at a high pressure, and an appropriate amount of lubricating oil is supplied to the thrust bearing 76.

The third housing body 64 has a suction chamber 64a formed on the center side thereof, and a discharge chamber 64b formed on the outer peripheral side.
The suction chamber 64a and the discharge chamber 64b are separated by a partition wall 64c.
The third housing 64 includes a suction port 84 that connects the suction chamber 64a and the refrigerant circuit C, and a discharge port 85 that connects the discharge chamber 64b and the refrigerant circuit C.
The refrigerant circuit C includes an oil separator 98 that separates and recovers the lubricating oil contained in the compressed high-pressure refrigerant.
A valve plate 90 is interposed between the first housing body 62 and the third housing body 64 that are joined to each other.
A compression chamber 91 is formed by the valve plate 90 and the cylinder bore 89.
A suction valve forming plate 83 is interposed between the first housing body 62 and the valve plate 90, and the suction valve forming plate 83 opens and closes a suction passage 90a formed in the valve plate 90 (not shown). It has.
A discharge valve forming plate 96 is interposed between the third housing body 64 and the valve plate 90. The discharge valve forming plate 96 includes a discharge valve 96 a that opens and closes a discharge passage 90 b formed in the valve plate 90.

The second housing body 63 includes a first shaft support portion 72.
The first shaft support portion 72 includes a radial bearing 74 and supports one end portion of the drive shaft 71 including the rotor 70.
The first housing body 62 has a body portion 62a and a lid portion 62b.
The lid portion 62 b includes a second shaft support portion 73 that supports the other end of the drive shaft 71, and the second shaft support portion 73 includes a thrust bearing 76 and a radial bearing 75.

A conversion mechanism accommodation chamber 77 is formed by the first housing body 62 and the second housing body 63, and the conversion mechanism 78 is accommodated in the conversion mechanism accommodation chamber 77.
A cylinder bore 89 is formed in the body portion 62 a of the first housing body 62, and the cylinder bore 89 is formed through the other end portion of the first housing body 62 from the conversion mechanism housing chamber 77.
A piston 92 that reciprocates in the cylinder bore 89 is provided, and the bottom of the piston 92 reaches the conversion mechanism housing chamber 77.

The conversion mechanism 78 of this embodiment includes a swash plate 80 fitted on the drive shaft 71 and a shoe 79 held on the neck of the piston 92. The shoe 79 is engaged and slid with respect to the outer periphery of the swash plate 80.
The swash plate 80 includes inclined surfaces 80 a and 80 b that are inclined with respect to the axis of the drive shaft 71.
The drive shaft 71 and the drive shaft 71 are spline-fitted so that they can slide with respect to the axial direction of the drive shaft 71.
Here, the fixed swash plate 80 has a constant tilt angle. However, for example, a variable swash plate capable of changing the tilt angle of the swash plate with respect to the axis of the drive shaft 71 may be used.
In this case, the inclination of the swash plate can be changed in accordance with the fluctuation of the pressure in the conversion mechanism accommodation chamber, and the capacity of the refrigerant compressed by the compressor can be changed.
A thrust bearing 81 is interposed between the second housing body 63 and the base of the swash plate 80.
A coil spring 82 as an urging member is fitted on the drive shaft 71 between the base of the rotor 70 and the swash plate 80.

In the compressor 60 of this embodiment, the drive shaft 71 is rotated by driving the electric motor 68, and the swash plate 80 is rotated together with the rotation of the drive shaft 71.
The position of the shoe 79 is displaced corresponding to the rotating swash plate 80, and the piston 92 is reciprocated.
In the suction process of the piston 92 toward the bottom dead center, the suction valve 83a is opened, and the low-pressure refrigerant before compression is sucked into the compression chamber 91 from the suction chamber 64a.
During the discharge process of the piston 92 toward top dead center, the discharge valve 96a is opened, and the compressed high-pressure refrigerant is discharged from the compression chamber 91 to the discharge chamber 64b.

The high-pressure refrigerant discharged into the discharge chamber 64b is sent to the refrigerant circuit C through the discharge port 85, but the lubricating oil contained in the high-pressure refrigerant is separated and recovered by the oil separator 98 included in the refrigerant circuit C.
A part of the lubricating oil is supplied to the bolt through hole 64 e of the third housing body 64 through the lubricating oil supply pipe 49 by utilizing the high pressure of the refrigerant in the oil separator 98.
The lubricating oil is supplied to the thrust bearing 76 in the second shaft support portion 75 through a bolt through hole 64e through which the joining bolt 67 is inserted and a bolt hole 62d into which the joining bolt 67 is screwed.
By supplying the lubricating oil to the thrust bearing 76, the lubricating oil is supplied to the radial bearing 75 in the vicinity of the thrust bearing 76.

The compressor 60 of this embodiment has the following effects.
The conversion mechanism 78 includes a swash plate 80 through which the drive shaft 71 is inserted and rotated together with the drive shaft 71, and an inclined surface inclined with respect to the axis of the drive shaft 71, and an outer peripheral portion of the swash plate 80. And a shoe 79 held on the neck of the piston 92 so that the swash plate 80 is slidable in the axial direction of the drive shaft. Thus, the rotational movement of the drive shaft 71 is converted into the reciprocating motion of the piston 92 via the shoe 39 by the swash plate 80 that rotates together with the drive shaft 71.

Next, another example of the first housing body in which the cylinder bore is formed will be described.
FIG. 7 shows other examples 1 and 2 of the first housing body, and is a front view of the first cylinder in each example as seen from the other end face.
A first housing body 101 of another example 1 shown in FIG. 7A has a substantially octagonal end surface, and nine cylinder bores 103 are formed so as to be positioned around the electric motor 102.
A bolt hole 105 for a joining bolt is formed in the center of the first housing body 101.
A bolt hole 106 for a joining bolt is formed between adjacent cylinder bores 103.
According to the first housing body 101 of this alternative example 1, since the strength can be improved by increasing the thickness of the housing body 101, it is suitable for compression of a high-pressure refrigerant.

Nine cylinder bores 113 are formed in the first housing body 111 of another example 2 shown in FIG. 7B so as to be located around the electric motor 112.
A bulging portion 111 a that follows the cylinder bore 113 is formed on the outer periphery of the first housing body 111.
The first housing body 111 is provided with a bolt hole 114 between the bolt hole 115 at the center and the cylinder bore 113 as in the first embodiment.
According to the first housing body 111 of this alternative example 2, the thickness of the first housing body 111 can be reduced.
Moreover, since the surface area of the outer peripheral surface of the 1st housing body 111 increases by formation of the bulging part 111a, the heat dissipation effect of the 1st housing body 111 can be anticipated.

It is a side view which cuts and shows the compressor of a 1st embodiment. It is the front view which looked at the 1st housing body of a 1st embodiment from the other end. FIG. 3 is an enlarged side view of the vicinity of the piston according to the first embodiment. It is a side view which shows the outline | summary of the universal joint and wobble plate of 1st Embodiment. It is the side view which shows the piston of another example, and the XX line view in a side view. It is a side view which shows the compressor concerning a 2nd embodiment longitudinally. It is the front view which looked at the 1st housing body concerning another example from the other end.

Explanation of symbols

10, 60 Compressor 11, 61 Housing 12, 62, 101, 111 First housing body 12d, 62d, 105, 115 Bolt hole 13, 63 Second housing body 14, 64 Third housing body 14e, 64f Lubricating oil passage 18 , 68, 102, 112 Electric motor 19, 69 Stator 20, 70 Rotor 21, 71 Drive shaft 22, 72 First shaft support portion 23, 73 Second shaft support portion 27, 77 Conversion mechanism accommodation chamber 28, 78 Conversion mechanism 30 Lug plate 31 Universal joint 32 Wobble plate 38 Communication passage 39, 89, 103, 113 Cylinder bore 40, 90 Valve plate 41, 91 Compression chamber 42, 54, 92 Piston 43, 57 Rod 44, 56 Suction valve 46a, 96a Discharge valve 48, 98 Oil separator 49, 97 Lubricating oil supply pipe 50, 82 Coil spring 4a suction chamber 70 shoe 80 swash plate

Claims (9)

An electric motor that rotates the drive shaft;
A conversion mechanism for converting rotational movement of the drive shaft into reciprocating movement in a substantially linear direction;
Connected to the conversion mechanism, provided outside the electric motor with respect to the drive shaft so as to surround the electric motor, reciprocating in conjunction with the reciprocating movement by the conversion mechanism, and compressible from an external circuit A compression mechanism including a piston that sucks fluid, compresses the fluid, and discharges the compressed fluid to an external circuit;
A compressor with each component housed in a single housing. The compressor according to claim 1, wherein the compression mechanism includes at least a compression chamber and the piston, and the compression chamber is formed in the housing. The compressor according to claim 2, wherein a central axis of the compression chamber is substantially parallel to an axis of the drive shaft. The housing is composed of at least two housings,
The first housing covers the electric motor, the compression chamber, a port for sucking compressive fluid from the external circuit, a passage connecting the port and the compression chamber, and the compression mechanism sucking A valve for communicating the port and the compression chamber when in the process;
The second casing is provided on a side opposite to the side where the conversion mechanism is provided with respect to the electric motor, and a discharge chamber is formed at a position facing the compression chamber. The discharge chamber and the external circuit And a port to connect
The compressor according to claim 2 or 3, wherein the compression chamber and the discharge chamber are communicated with each other, and a valve is provided for communicating between the compression chamber and the discharge chamber when the compression mechanism is in the discharge process. The first casing and the second casing are connected by bolts at least on a straight line substantially the same as the axis of the drive shaft,
The compressor according to claim 4, further comprising a lubricating oil supply mechanism that supplies lubricating oil to at least the drive shaft by using the screw groove for the bolt. The compressor according to any one of claims 1 to 5, wherein the conversion mechanism is a wobble type conversion mechanism or a swash plate type conversion mechanism. The biasing member which applies a force in the direction which is substantially coincident with the axis of the drive shaft and away from the electric motor is further provided for the conversion mechanism. Compressor. Of the members that are provided around the electric motor and move relatively with respect to the housing, a member that is substantially affected by the magnetic force from the electric motor when made of a magnetic material is non-magnetic. The compressor according to any one of claims 1 to 7, wherein the compressor is a material. The compressor according to claim 7, wherein the biasing member is a nonmagnetic material.

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