JP4865417B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor.

In the scroll compressor, the fixed scroll and the orbiting scroll are engaged with each other in the housing, a plurality of compression chambers are formed, and the orbiting scroll is driven to revolve orbit to reduce the volume of the compression chamber from the outer peripheral position to the center position. It is configured to compress the fluid by moving it.
In order to drive the orbiting scroll to revolve with respect to the fixed scroll, a crankshaft is provided in the housing so as to be rotatable about its axis. One end portion of the crankshaft is provided with a large-diameter shaft portion. The large-diameter shaft portion is further connected to an orbiting scroll via a drive bush or the like, and an eccentric pin that orbits the orbiting scroll member with a predetermined orbiting radius. Is provided. The crankshaft is supported so as to be rotatable about an axis line by supporting a large-diameter shaft portion on a housing via a main bearing constituted by a ball bearing disclosed in Patent Document 1, for example.
A seal member that seals the inside and outside of the housing is provided on the other end side of the crankshaft.

For example, in some scroll compressors used in a refrigeration cycle, a refrigerant to be sucked is introduced between an inner ring and an outer ring, and lubrication is performed with a lubricating oil contained therein.
In the case of a ball bearing, since it is a point contact, it has a relatively large structure corresponding to the load to be supported, and therefore a gap that can sufficiently introduce this refrigerant can be secured. On the other hand, there is a problem that the housing becomes large.
In this type of scroll compressor, since it is required to be as small and light as possible in terms of installation, for example, a needle roller bearing with an outer ring as shown in Patent Document 2 is used as a main bearing. There are proposals to reduce the size.
If a needle roller bearing with an outer ring is used, the introduction of the refrigerant becomes insufficient, and there is a possibility that sufficient lubrication cannot be performed.
Therefore, the thing shown by patent document 2 has secured the clearance gap where a refrigerant | coolant is introduce | transduced by devising the shape of the axial direction edge part of an outer ring | wheel.

Japanese Patent No. 2868998 JP 2000-2250 A

  However, the one disclosed in Patent Document 2 has a problem that the manufacturing cost increases because it is necessary to use a needle roller bearing with an outer ring having a special shape.

  In view of the above-described problems, an object of the present invention is to provide a scroll compressor that can be manufactured at low cost using a general-purpose needle roller bearing with an outer ring, and that can reduce the size and weight of a housing.

In order to solve the above problems, the present invention employs the following means.
That is, a scroll compressor according to the present invention includes a housing, a fixed scroll fixedly supported in the housing, and a compression mechanism having a revolving orbiting motion that is engaged with the fixed scroll and forms a plurality of compression chambers. And a large-diameter shaft portion having an eccentric member that revolves the orbiting scroll at one end, and the large-diameter shaft portion is rotatably supported by the housing via a needle roller bearing with an outer ring. And a seal member that is disposed on the other end side of the crankshaft and seals the inside and outside of the housing, and is provided between the orbiting scroll and the large-diameter shaft portion, and a fluid containing lubricating oil is sucked in. And a crank compressor, wherein an end position on one end side of the outer peripheral surface of the large-diameter shaft portion is a position of the outer ring. Than the end position of the end side is located at the other end, the one end of the outer peripheral surface of the large diameter portion from the inner surface of the first flange portion which is bent substantially at right angles toward the inside at one end of the outer ring A certain distance is provided in the axial direction of the outer ring until the end position on the side .

As described above, the end position on one end side of the outer peripheral surface of the large-diameter shaft portion is positioned on the other end side relative to the end position on one end side of the outer ring, so one end side on the outer peripheral surface of the large-diameter shaft portion A gap is formed between the outer ring and the end on one end side of the outer ring.
Since the fluid containing lubricating oil introduced into the crank chamber is introduced into the needle roller bearing with outer ring through this gap, the needle roller bearing with outer ring should be cooled with fluid and lubricated with lubricating oil. Can do.
As described above, since the gap for introducing the fluid is ensured by setting the end position on the one end side on the outer peripheral surface of the large-diameter shaft portion, the needle roller bearing with the outer ring may be a general-purpose one. It can be manufactured at low cost.
Further, since the needle roller bearing with the outer ring is used, the housing can be reduced in size and weight.

Moreover, in the said invention, the edge part position of the other end side in the outer peripheral surface of the said large diameter shaft part is located in the one end side rather than the edge part position of the other end side of the said outer ring | wheel, A certain distance is provided in the axial direction of the outer ring between the inner surface of the second flange portion bent at a substantially right angle toward the inner side and the end position on the other end side of the outer peripheral surface of the large-diameter shaft portion. it is preferable that is.
In this case, the fluid containing the lubricating oil is supplied to the seal member through a gap formed between the other end side of the outer peripheral surface of the large-diameter shaft portion and the end portion on the other end side of the outer ring. Further, cooling and lubrication of the seal member can be performed more reliably.

In addition, a scroll compressor according to the present invention includes a housing, a fixed scroll fixedly supported in the housing, and a compression mechanism having a revolving orbiting motion engaged with the fixed scroll and forming a plurality of compression chambers. And a large-diameter shaft portion having an eccentric member that revolves the orbiting scroll at one end, and the large-diameter shaft portion is rotatably supported by the housing via a needle roller bearing with an outer ring. And a seal member that is disposed on the other end side of the crankshaft and seals the inside and outside of the housing, and between the swiveling roll and the large-diameter shaft portion, and a fluid containing lubricating oil is sucked in. And a crank compressor, wherein the axial dimension of the outer peripheral surface of the large-diameter shaft portion is in the axial direction of the outer ring. It is shorter than the law, between the inner surface of the first flange portion which is bent substantially at a right angle at one end towards the inside of the outer ring to the end position of the one end side of the outer peripheral surface of the large diameter shaft portion The other end side of the outer peripheral surface of the large-diameter shaft portion from the inner surface of the second flange portion, which is provided with a certain distance in the axial direction of the outer ring and bent at a substantially right angle toward the inside at the other end of the outer ring A certain distance is provided in the axial direction of the outer ring until the end position .

As described above, since the dimension in the axial direction on the outer peripheral surface of the large-diameter shaft portion is shorter than the dimension in the axial direction of the outer ring, at least one end on the outer peripheral surface of the large-diameter shaft portion and one end on the one end side of the outer ring. A gap is formed between the portions.
Since the fluid containing lubricating oil introduced into the crank chamber is introduced into the needle roller bearing with outer ring through this gap, the needle roller bearing with outer ring should be cooled with fluid and lubricated with lubricating oil. Can do.
In this way, since the gap for introducing the fluid is ensured by setting the axial dimension on the outer peripheral surface of the large-diameter shaft portion to be predetermined, the needle roller bearing with the outer ring is inexpensive because it can be a general purpose one. Can be manufactured.
Further, since the needle roller bearing with the outer ring is used, the housing can be reduced in size and weight.
Further, depending on the dimensions, a gap can be formed between the other end side of the outer peripheral surface of the large-diameter shaft portion and the end portion on the other end side of the outer ring, so that sealing is performed by a fluid containing lubricating oil that has passed through the gap. The member can be cooled and lubricated more reliably.

Moreover, in the said invention, it is suitable for the one end part of the said large diameter shaft part to be equipped with the notch part notched toward the one end part from the said outer peripheral surface.
If it does in this way, the axial direction length of a large-diameter shaft part can be secured, after ensuring the crevice between an outer ring.

According to the present invention, the fluid is introduced between one end side of the outer peripheral surface of the large-diameter shaft portion and one end portion of the outer ring by setting one end position or axial length of the large-diameter shaft portion to a predetermined value. since ensuring a gap can, needle roller bearings with the outer ring can be divided inexpensively manufactured requires only one general-purpose.
Further, since the needle roller bearing with the outer ring is used, the housing can be reduced in size and weight.

Hereinafter, an embodiment of the present invention will be described with reference to FIGS. The scroll compressor 1 concerning this embodiment is used for compression of the refrigerant gas (fluid) of an air conditioner, for example.
FIG. 1 is a cross-sectional view illustrating a configuration of a scroll compressor 1 according to the present embodiment. FIG. 2 is a cross-sectional view showing a part of the large-diameter shaft portion in a broken state.
The scroll compressor 1 includes a housing 3, a scroll compression mechanism (compression mechanism) 5, a rotation prevention unit 7, and a crankshaft 9.

As shown in FIG. 1, the housing 3 is a sealed container in which a scroll compression mechanism 5 and the like are arranged.
The housing 3 is provided with a rear case 11 constituting a rear (upper side in FIG. 1) and a front case 13 constituting a front (lower side in FIG. 1) part.
The rear case 11 has a substantially hollow dome shape, and is made of an aluminum alloy and formed by casting.
The front case 13 has a shape in which a hollow cylinder and a truncated cone are combined, and is made of an aluminum alloy and formed by casting.
The rear case 11 and the front case 13 are joined together by fastening with bolts 15, and a sealed space (suction space) M is formed inside.

The scroll compression mechanism 5 includes a fixed scroll 17 and a turning scroll 19.
The fixed scroll 17 includes a fixed end plate 21 and a spiral fixed spiral body 23 erected on the front surface thereof.
On the rear side of the fixed end plate 21, there are formed a recess 25 that is recessed forward in the center and a rear end surface 27 that surrounds the recess 25 in an annular shape.

The rear end surface 27 is abutted with an end surface 29 provided in an annular shape on the front surface of the rear case 11, and the fixed scroll 17 is fixedly attached to the rear case 11 by joining a plurality of locations with bolts 31.
At this time, since the rear case 11 and the fixed scroll 17 are sealed from the sealed space M by a seal 33 such as an O-ring over the entire outer peripheral side, the hollow portion of the rear case 11 and the concave portion 25 of the fixed end plate 21 A discharge chamber 35 is formed.
A compressed fluid discharge port 37 is formed at a substantially central portion of the recessed portion 25 of the fixed end plate 21. The discharge port 37 is opened and closed by a discharge valve (not shown) attached to the rear surface of the fixed end plate 21, and discharges the compressed fluid into the discharge chamber 35.

A suction boss portion 39 is provided at the front end portion of the cylindrical portion of the front case 13.
The suction boss portion 39 is excavated with a suction port portion 41 that communicates with the sealed space M and introduces refrigerant gas (fluid) from the outside into the sealed space M.

The orbiting scroll 19 includes an orbiting end plate 43 and a spiral orbiting spiral body 45 standing on the rear surface thereof.
The orbiting scroll 19 is installed such that the orbiting spiral body 45 meshes with the fixed spiral body 23.
The fixed scroll 17 and the orbiting scroll 19 are point-symmetric with respect to the centers of the fixed spiral body 23 and the orbiting spiral body 45 by being engaged with each other with a phase difference of 180 degrees while being eccentric from each other by a predetermined distance. Compression chambers P serving as sealed spaces are formed at a plurality of locations having the positional relationship.
A hollow cylindrical swivel boss 47 is provided at the center of the front surface of the swivel end plate 45 (lower surface center in FIG. 1) so as to protrude forward.

The orbiting scroll 19 is supported on the front case 13 so as to be able to perform a revolving orbit with respect to the fixed scroll 17.
The rotation prevention unit 7 includes a plurality of rings 49 and a plurality of pins 51.
The respective rings 49 are respectively provided in a plurality of ring holes 53 provided on the outer peripheral side of the front end face of the orbiting end plate 43 and at substantially equal intervals on the circumference of a predetermined radius from the center of the orbiting scroll 19. It is press-fitted or loosely fitted.

The number of pins 51 is the same as the number of the rings 49, and each pin 51 is fitted on the rear end surface of the truncated cone portion of the front case 13 so as to protrude into the corresponding ring 49.
The orbiting scroll 19 is engaged with the front case 13 when the pin 51 is loosely inserted into the ring 49, and is prevented from rotating when revolving. At this time, the pin 51 rotates along the inner peripheral surface of the ring 49 in the same direction as the revolution direction of the orbiting scroll 19.
In addition, as the rotation prevention part 7, you may use a well-known Oldham ring, for example.

The crankshaft 9 is disposed so as to extend in the front-rear direction, and an outer peripheral surface 57 of a large-diameter shaft portion 55 provided on the rear side is interposed through a large-diameter shaft portion needle bearing (needle roller bearing with an outer ring) 59 in the front case. 13 is rotatably supported.
As shown in FIG. 2, the large-diameter shaft needle bearing 59 includes an outer ring 61, a cage 63, and a plurality of needle rollers 65.
The outer ring 61 has a substantially hollow cylindrical shape, and is formed with a rear collar part 67 and a front collar part 69 which are bent at substantially right angles toward the inside at both ends in the axial direction J of the crankshaft 9.
The cage 63 holds a plurality of needle rollers 65 at substantially equal intervals in the circumferential direction, and is attached to the inner side of the outer ring 61.

The large-diameter shaft needle bearing 59 is held by being closely fitted in a recess 71 provided in a substantially intermediate portion in the axial direction J of the conical portion of the front case 13.
Both ends of the large-diameter shaft portion 55 in the axial direction J are chamfered. The inner portion of the chamfer constitutes the outer peripheral surface 57.
The rear end position (end position on one end side) A of the outer peripheral surface 57 is positioned on the front (other end) side of the front end position (end position on one end side) C of the rear collar 67.
Further, the front end position (end position on the other end side) B of the outer peripheral surface 57 is positioned on the rear (one end) side of the front end position (end position on the other end side) D of the front collar portion 69. Yes.

Further, the axial direction J length L1 of the outer peripheral surface 57 is configured to be shorter than the axial direction J length L2 of the outer ring 61.
Since the axial position J intermediate position of the outer peripheral surface 57 and the outer ring 61 is substantially aligned, the above-described gaps are provided on the front and rear sides, respectively.
The gap between the front end position B of the outer peripheral surface 57 and the front end position D of the front collar portion 69 is provided for lubrication of the lip seal 75. When lubrication means is separately provided and lubrication of the lip seal 75 is not required. However, this gap may not be provided.
In addition, the axial direction J length L1 of the outer peripheral surface 57 is formed so as to be longer than the length of the needle roller 65 so that a biased load is not applied to the needle roller 65.

The front end of the crankshaft 9 projects forward from the front case 13 and is rotatably attached by a ball bearing 73 provided at the front end of the front case 13.
The rear side of the ball bearing 73 of the crankshaft 9 is sealed between the sealed space M and the outside by a lip seal (seal member) 75 formed of a mechanical seal.
The front end portion of the crankshaft 9 protruding from the front case 13 is configured to be rotated by driving means such as an engine or a motor (not shown).

A crank chamber 81 in which the turning boss 47 is fitted with a margin is provided at the rear center of the conical portion of the front case 13.
The rear end portions of the large-diameter shaft needle bearing 59 and the large-diameter shaft portion 55 face the crank chamber 81.
On the rear side of the large-diameter shaft portion 55 of the crankshaft 9, an eccentric shaft (eccentric member) 83 whose axis center is eccentric is provided so as to be positioned in the hollow portion of the turning boss 47.
A counterweight 85 is provided around the eccentric shaft 83. The counterweight 85 is disposed in the crank chamber 81 so as to cover around the eccentric shaft 83 and the front end portion extends in a direction opposite to the eccentric direction of the eccentric shaft 83 (left direction in FIG. 1) (right direction in FIG. 1). The large-diameter shaft portion 55 is fixedly attached.

An eccentric bushing 87 is rotatably fitted to a hollow portion of the turning boss 47 via a needle bearing 89 so as to cover a cylindrical counterweight 85 located in the turning boss 47.
The center line of the eccentric bush 87 is eccentric with respect to the center line of the crankshaft 9.
The eccentric bush 87 has a function of transmitting the rotational driving force of the crankshaft 9 to the orbiting scroll 19 and driving the orbiting scroll 19 to revolve.

The compression operation of the scroll compressor 1 configured as described above will be described.
A rotational driving force from an engine, an electric motor, or the like (not shown) is transmitted to the crankshaft 9, and this rotational driving force is turned by the scroll compression mechanism 5 via the eccentric shaft 83, the counterweight 85, the eccentric bush 87, and the turning boss 47. It is transmitted to the scroll 19.
The orbiting scroll 19 is prevented from rotating by the rotation preventing unit 7 and is driven to perform a revolving orbiting motion on a circular orbit having a revolving orbiting radius as a radius.

When the orbiting scroll 19 is driven to revolve, the refrigerant gas enters the sealed space M of the housing 3 through the suction port 41 and is sucked into the compression chamber P of the scroll compression mechanism 5.
At this time, since the lubricating oil contained in the refrigerant gas is introduced into the compression chamber P along with the refrigerant gas, the scroll compression mechanism 5 is lubricated.
Then, as the volume of the compression chamber P decreases due to the revolving orbiting motion of the orbiting scroll 19, the refrigerant gas reaches the central compression chamber P while being compressed.
The compressed refrigerant gas reaching the central compression chamber P is discharged from the discharge port 37 to the discharge chamber 35.
The compressed refrigerant gas discharged into the discharge chamber 35 is supplied to the radiator through a discharge hole (not shown).

At this time, the counterweight 85 is rotated by the eccentric shaft 83 of the crankshaft 9 in a state that is approximately 180 degrees out of phase with the revolutionary orbiting motion of the orbiting scroll 19. Therefore, the centrifugal force acting on the orbiting scroll 19 is canceled by the counterweight 85, and the dynamic imbalance is reduced.
Further, since the orbiting scroll 19 revolves while the counterweight 85 rotates, the tip of the counterweight 85 disposed in the crank chamber 81 relatively rotates in the crank chamber 81.

Next, the lubrication operation related to the crankshaft 9 will be described.
The low-temperature and low-pressure refrigerant gas sucked into the sealed space M flows into the crank chamber 81 constituting the sealed space M.
The refrigerant gas containing lubricating oil that has flowed into the crank chamber 81 is introduced into the large-diameter shaft needle bearing 59 through a gap between the rear end position A of the outer peripheral surface 57 and the front end position C of the rear collar portion 67. Is done.
Since the large-diameter shaft needle bearing 59 is cooled and lubricated by the refrigerant gas and the lubricating oil, the temperature in the sealed space M is made uniform and the lubricity can be improved.

The refrigerant gas introduced into the large-diameter shaft needle bearing 59 reaches the lip seal 75 through the gap between the front end position B of the outer peripheral surface 57 and the front end position D of the front collar portion 69, and cools the lip seal 75. Lubricate.
Thus, by positioning the rear end position A of the outer peripheral surface 57 of the large-diameter shaft portion 55 in front of the front-end position C of the rear collar portion 67, a gap for introducing the refrigerant gas into the large-diameter shaft portion needle bearing 59 is provided. Since the front end position B of the outer peripheral surface 57 is set behind the front end position D of the front collar portion 69, a gap for introducing the refrigerant gas to the lip seal 75 is ensured. The partial needle bearing 59 can be manufactured inexpensively as long as it is a general purpose one.

On the other hand, the refrigerant introduced into the crank chamber 81 is introduced into the needle bearing 89 and used for cooling and lubricating the needle bearing 89 and the like.
Further, since the large-diameter shaft portion needle bearing 59 is used, it is necessary to enlarge the front case 13 more than necessary, and the housing can be reduced in size and weight.

In this embodiment, the front and rear ends of the large-diameter shaft portion 55 are chamfered, but as shown in FIG. 4, a large notch 77 having a rectangular section that is continuous in the circumferential direction is shown in FIG. You may make it provide the big notch part 77 with such a triangular cross section.
Further, the cross-sectional shape of the notch 77 is not limited to this and may be any shape. Furthermore, it may be discontinuous in the circumferential direction.
In this way, it is possible to increase the length of the large-diameter shaft portion 55 in the axial direction J while ensuring a gap between the large-diameter shaft portion needle bearing 59 and the outer ring 61.

It is sectional drawing which shows the whole schematic structure of the scroll compressor concerning one Embodiment of this invention. It is a fragmentary sectional view which shows the relationship between the large diameter axial part needle bearing concerning one Embodiment of this invention, and a large diameter axial part. It is a fragmentary sectional view which shows the part similar to FIG. It is a fragmentary sectional view similar to FIG. 2 which shows another embodiment of the large diameter axial part concerning one Embodiment of this invention. It is a fragmentary sectional view similar to FIG. 2 which shows another embodiment of the large diameter axial part concerning one Embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Scroll compressor 3 Housing 5 Scroll compression mechanism 9 Crankshaft 17 Fixed scroll 19 Orbiting scroll 55 Large diameter shaft part 57 Outer peripheral surface 59 Large diameter shaft part Needle bearing 75 Lip seal 77 Notch part 81 Crank chamber 83 Eccentric shaft A Rear end position B Front end position C Tip position D Tip position M Sealed space P Compression chamber

Claims (5)

A housing;
A fixed scroll that is fixedly supported in a housing, and a compression mechanism that is engaged with the fixed scroll and has a revolving orbiting motion by forming a plurality of compression chambers;
A crankshaft provided at one end with a large-diameter shaft portion having an eccentric member for revolving orbiting the orbiting scroll, the large-diameter shaft portion being rotatably supported by the housing via a needle roller bearing with an outer ring;
A seal member disposed on the other end side of the crankshaft and sealing the inside and outside of the housing;
A scroll compressor provided between the orbiting scroll and the large-diameter shaft portion, and a crank chamber into which a fluid containing lubricating oil is sucked,
An end position on one end side of the outer peripheral surface of the large-diameter shaft portion is located on the other end side than an end position on one end side of the outer ring ,
Constant in the axial direction of the outer ring from the inner surface of the first flange part bent at a substantially right angle toward the inside at one end of the outer ring to the end position on one end side of the outer peripheral surface of the large-diameter shaft part. A scroll compressor characterized in that a distance of is provided . The end position on the other end side of the outer peripheral surface of the large-diameter shaft portion is located on one end side with respect to the end position on the other end side of the outer ring ,
The axial direction of the outer ring between the inner surface of the second flange part bent at a substantially right angle toward the inside at the other end of the outer ring and the end position on the other end side of the outer peripheral surface of the large-diameter shaft part. The scroll compressor according to claim 1 , wherein a certain distance is provided in the scroll compressor. A housing;
A fixed scroll that is fixedly supported in a housing, and a compression mechanism that is engaged with the fixed scroll and has a revolving orbiting motion by forming a plurality of compression chambers;
A crankshaft provided at one end with a large-diameter shaft portion having an eccentric member for revolving orbiting the orbiting scroll, the large-diameter shaft portion being rotatably supported by the housing via a needle roller bearing with an outer ring;
A seal member disposed on the other end side of the crankshaft and sealing the inside and outside of the housing;
A scroll compressor provided between the revolving roll and the large-diameter shaft portion, and a crank chamber into which a fluid containing lubricating oil is sucked,
The axial dimension of the outer peripheral surface of the large-diameter shaft portion is shorter than the axial dimension of the outer ring ,
Constant in the axial direction of the outer ring from the inner surface of the first flange part bent at a substantially right angle toward the inside at one end of the outer ring to the end position on one end side of the outer peripheral surface of the large-diameter shaft part. A distance of
The axial direction of the outer ring between the inner surface of the second flange part bent at a substantially right angle toward the inside at the other end of the outer ring and the end position on the other end side of the outer peripheral surface of the large-diameter shaft part. A scroll compressor characterized in that a certain distance is provided in the scroll compressor.   The one end part of the said large diameter shaft part is provided with the notch part notched toward the one end part from the said outer peripheral surface, It was described in any one of Claim 1 to 3 characterized by the above-mentioned. Scroll compressor.   The inner surface of the first flange portion is not in the same virtual plane as an end portion position on one end side of the outer peripheral surface of the large-diameter shaft portion, according to any one of claims 1 to 4. Scroll compressor.

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