阅读说明：本技术 包括具有上凹部的曲柄销的涡旋压缩机 (Scroll compressor including crank pin having upper recess ) 是由 雷米·布达尔汗姆 阿诺德·多森 多米尼克·格罗斯 于 2020-11-03 设计创作，主要内容包括：涡旋压缩机包括：静涡旋盘,该静涡旋盘具有静端板和从静端板延伸出的静螺旋涡卷；动涡旋盘(9),该动涡旋盘(9)具有动端板和从动端板延伸出的动螺旋涡卷,静螺旋涡卷和动螺旋涡卷彼此接合以形成压缩室；竖直驱动轴(19),该竖直驱动轴(19)具有位于竖直驱动轴(19)的上端部处的曲柄销(21),该曲柄销(21)包括与动涡旋支承件(24)协作的外周表面(23)。曲柄销(21)包括形成在曲柄销(21)的轴向端面(26)中的凹部(25),该凹部(25)和外周表面(23)的上部(27)之间限定出周向壁(28),该周向壁(28)沿着曲柄销(21)的周边的至少一部分延伸,周向壁(28)能够在涡旋压缩机的运行期间沿径向方向变形。(The scroll compressor includes: a fixed scroll having a fixed end plate and a fixed spiral wrap extending from the fixed end plate; a movable scroll (9), the movable scroll (9) having movable spiral wraps extending from a movable end plate and a driven end plate, the stationary spiral wrap and the movable spiral wrap engaging with each other to form a compression chamber; a vertical drive shaft (19), the vertical drive shaft (19) having a crank pin (21) at an upper end of the vertical drive shaft (19), the crank pin (21) comprising an outer peripheral surface (23) cooperating with an orbiting scroll support (24). The crank pin (21) includes a recess (25) formed in an axial end face (26) of the crank pin (21), the recess (25) and an upper portion (27) of the outer peripheral surface (23) defining a circumferential wall (28) therebetween, the circumferential wall (28) extending along at least a portion of a periphery of the crank pin (21), the circumferential wall (28) being deformable in a radial direction during operation of the scroll compressor.)

1. A scroll compressor (2) comprising:

-a fixed scroll (8), the fixed scroll (8) having a fixed end plate (11) and a fixed spiral wrap (12) extending from the fixed end plate (11);

-a moving scroll (9), said moving scroll (9) having a moving end plate (13) and a moving spiral wrap (14) extending from said moving end plate (13), said stationary spiral wrap (12) and said moving spiral wrap (14) engaging each other to form a compression chamber (15);

-a vertical drive shaft (19), said vertical drive shaft (19) having a crank pin (21) at an upper end of said vertical drive shaft (19), said crank pin (21) comprising an outer peripheral surface (23) cooperating with an orbiting scroll support (24);

wherein the crank pin (21) includes a recess (25) formed in an axial end face (26) of the crank pin (21), the recess (25) and an upper portion (27) of the outer peripheral surface (23) defining a circumferential wall (28) therebetween, the circumferential wall (28) extending along at least a portion of a periphery of the crank pin (21), the circumferential wall (28) being deformable in a radial direction during operation of the scroll compressor (2).

2. The scroll compressor (2) of claim 1, wherein the circumferential wall (28) has a curved shape.

3. A scroll compressor (2) as claimed in claim 1 or 2, wherein the circumferential wall (28) has a substantially constant thickness along its circumference.

4. A scroll compressor (2) as claimed in any one of claims 1 to 3, wherein the recess (25) is radially offset from the outer peripheral surface (23) of the crank pin (21).

5. A scroll compressor (2) as claimed in any one of claims 1 to 4, wherein the circumferential wall (28) extends at least in a region (30) in which the bearing load (F) exerted on the outer peripheral surface (23) of the crank pin (21) is greatest.

6. A scroll compressor (2) as claimed in any one of claims 1 to 5, wherein the circumferential wall (28) extends over an angle of at least 120 ° centred on a crank pin axis (B) of the crank pin (21) between a first predetermined circumferential position (P1) and a second predetermined circumferential position (P2).

7. A scroll compressor (2) as claimed in claim 6, wherein the first predetermined circumferential position (P1) lies in a first half-space defined by a reference plane (P) including the crankpin axis (B) and the axis of rotation (A) of the vertical drive shaft (19), and the second predetermined circumferential position (P2) lies in a second half-space defined by the reference plane (P).

8. A scroll compressor (2) as claimed in claim 6 or 7, wherein a first orthogonal projection of the first predetermined circumferential position (P1) in a projection plane orthogonal to the crankpin axis (B) and to the axis of rotation (A) of the vertical drive shaft (19) and a reference half-line define a first angle (a), the reference half-line comprises an initial point corresponding to an orthogonal projection of the crankpin axis (B) in the projection plane, and the reference half-line passes through a reference point corresponding to the orthogonal projection of the axis of rotation (A) of the vertical drive shaft (19) in the projection plane, said first angle (a) being centered on said initial point and between 0 ° and 180 °, for example between 0 ° and 60 °, the first angle (α) being measured from the reference half-line in a first measuring direction.

9. A scroll compressor (2) as claimed in claim 8, wherein a second orthogonal projection of the reference half-line and the second predetermined circumferential position (P2) in the projection plane defines a second angle (β) centered on the initial point and between 90 ° and 180 °, such as between 90 ° and 150 °, the second angle (β) being measured from the reference half-line in a second measurement direction opposite to the first measurement direction.

10. A scroll compressor (2) as claimed in claim 6, wherein the first and second predetermined circumferential positions (P1, P2) are substantially the same such that the circumferential wall (28) extends over an angle of about 360 °.

11. The scroll compressor (2) of any of claims 1 to 10, wherein the circumferential wall (28) has a thickness and a height configured to ensure pure elastic deformation of the circumferential wall (28) during operation of the scroll compressor (2).

12. A scroll compressor (2) as claimed in any of claims 1 to 11, wherein the recess (25) has a depth configured such that the circumferential wall (28) axially overlaps at least a portion of the orbiting scroll support (24).

13. A scroll compressor (2) as claimed in any of claims 1 to 12, wherein the recess (25) is formed by a groove.

14. A scroll compressor (2) as claimed in any of claims 1 to 13, wherein the recess (25) has a substantially semi-circular disc shape.

15. A scroll compressor (2) as claimed in any one of claims 1 to 14, wherein the circumferential wall (28) has an upper edge (29), the upper edge (29) having a tapered or rounded shape.

16. A vertical drive shaft (19) for a scroll compressor (2), the vertical drive shaft (19) having a crank pin (21) at an upper end of the vertical drive shaft (19), the crank pin (21) comprising an outer peripheral surface (23), the outer peripheral surface (23) being configured to cooperate with an orbiting scroll support (24), wherein the crank pin (21) comprises a recess (25) formed in an axial end surface (26) of the crank pin (21), the recess (25) and an upper portion (27) of the outer peripheral surface (23) defining a circumferential wall (28) therebetween, the circumferential wall (28) extending along at least a portion of a circumference of the crank pin (21).

Technical Field

The invention relates to a scroll compressor, in particular to a scroll refrigeration compressor.

Background

As is well known, a scroll compressor includes:

-a fixed scroll having a fixed end plate and a fixed spiral wrap (wrap) extending from the fixed end plate;

-an orbiting scroll having an orbiting spiral wrap extending from an orbiting end plate and a driven end plate, the stationary spiral wrap and the orbiting spiral wrap being engaged with each other to form a compression chamber;

-a vertical drive shaft having a crank pin at an upper end of the vertical drive shaft, the crank pin comprising an outer peripheral surface cooperating with an orbiting scroll support provided on the orbiting scroll.

Typically, during operation of a scroll compressor, the orbiting scroll has a tendency to perform a tilting or oscillating motion. This tilting motion is due to different forces acting on the orbiting scroll at different axial and/or radial positions, such as gas forces in the compression chamber, friction forces or inertial forces generated in the vertical drive shaft support.

This oscillating movement may cause undesirable loads on the drive shaft bearings mounted in the static compressor element (in particular in the lower and upper main bearing supports) due to the deformation of the vertical drive shaft itself.

Furthermore, considerable edge loading effects are observed between the orbiting scroll support mounted in the connecting sleeve portion (also referred to as hub) of the orbiting scroll and the crank pin of the vertical drive shaft, which may damage the integrity of the orbiting scroll support.

US5076772 discloses a scroll compressor comprising a orbiting scroll having a boss received in a bore of a slider block received in an elongated recess provided in an axial end face of a vertical drive shaft. In particular, the slider comprises a deformable pad circumferentially arranged in the contact surface between the boss of the orbiting scroll and the slider. The deformable pads collectively define a deflecting support that allows relative tilting between the orbiting scroll and the vertical drive shaft without generating side loads when the vertical drive shaft is rotated about its axis of rotation.

However, the manufacturing cost of such a slider block is relatively high, which significantly increases the manufacturing cost of the scroll compressor.

Disclosure of Invention

It is an object of the present invention to provide an improved scroll compressor which overcomes the disadvantages encountered in conventional scroll compressors.

It is another object of the present invention to provide a scroll compressor having a simple and economical structure with an increased life of the orbiting scroll support.

According to the present invention, such a scroll compressor comprises:

-a fixed scroll having a fixed end plate and a fixed spiral wrap extending from the fixed end plate;

-an orbiting scroll having an orbiting spiral wrap extending from an orbiting end plate and a driven end plate, the stationary spiral wrap and the orbiting spiral wrap being engaged with each other to form a compression chamber;

-a vertical drive shaft having a crank pin at an upper end thereof, the crank pin comprising an outer peripheral surface cooperating with the orbiting scroll support;

wherein the crank pin includes a recess formed in an axial end face of the crank pin, the recess and an upper portion of the outer peripheral surface defining a circumferential wall therebetween, the circumferential wall extending along at least a portion of a circumference of the crank pin, the circumferential wall being deformable in a radial direction relative to a crank pin axis of the crank pin during operation of the scroll compressor, and particularly when the orbiting scroll performs a tilting or oscillating motion and exerts a contact pressure on the circumferential wall.

Such a circumferential wall defining a crankpin portion having reduced stiffness and being deformable in the radial direction when the orbiting scroll performs a tilting or oscillating motion significantly reduces the contact pressure between the orbiting scroll support and the outer peripheral surface of the crankpin, and thus increases the service life of the orbiting scroll support without the use of a complicated drive shaft support.

The scroll compressor may also include one or more of the following features, either alone or in combination.

According to an embodiment of the invention, the circumferential wall has a curved shape, and for example a substantially arcuate shape or an annular shape.

According to an embodiment of the invention, the circumferential wall has a substantially constant thickness along its circumference.

According to an embodiment of the present invention, the circumferential wall includes an inner circumferential wall surface and an outer circumferential wall surface, the outer circumferential wall surface being defined by an outer circumferential surface of the crank pin.

According to an embodiment of the invention, the inner circumferential wall surface and the outer circumferential wall surface are substantially parallel with respect to each other.

Advantageously, the inner and outer circumferential wall surfaces are centered on a crank pin axis of the crank pin.

According to an embodiment of the invention, the inner circumferential wall surface is cylindrical.

According to an embodiment of the present invention, an outer peripheral surface of the crank pin is cylindrical.

According to an embodiment of the present invention, the inner circumferential wall surface diverges from the bottom surface of the recess toward the axial end face of the crank pin.

According to an embodiment of the invention, the recess is radially offset with respect to an outer circumferential surface of the crank pin. This configuration of the recess ensures that the outer peripheral surface of the crank pin, which cooperates with the orbiting scroll support, is retained.

According to an embodiment of the present invention, the circumferential wall extends at least in a region where a bearing load applied on the outer circumferential surface of the crank pin is maximum.

According to an embodiment of the invention, the circumferential wall extends between the first predetermined circumferential position and the second predetermined circumferential position over an angle of at least 120 ° and for example around 180 ° centered around the crank pin axis of the crank pin.

According to an embodiment of the invention, the first predetermined circumferential position is located in a first half-space defined by a reference plane comprising the crank pin axis and the rotation axis of the vertical drive shaft, and the second predetermined circumferential position is located in a second half-space defined by the reference plane.

According to an embodiment of the invention, a first orthogonal projection of the first predetermined circumferential position in a projection plane orthogonal to the crankpin axis and to the rotation axis of the vertical drive shaft and a reference half-line, which passes through a reference point corresponding to the orthogonal projection of the rotation axis of the vertical drive shaft in the projection plane, define a first angle centered on said initial point and between 0 ° and 180 °, for example between 0 ° and 60 °, measured from the reference half-line in the first measurement direction, in a projection plane orthogonal to the crankpin axis and to the rotation axis of the vertical drive shaft.

According to an embodiment of the invention, the first angle is between 30 ° and 60 °, for example about 45 °.

According to an embodiment of the invention, a second orthogonal projection of the reference half-line and the second predetermined circumferential position in the projection plane defines a second angle, centered on said initial point and between 90 ° and 180 °, for example between 90 ° and 150 °, the second angle being measured from the reference half-line in a second measurement direction opposite to the first measurement direction.

According to an embodiment of the invention, the second angle is between 110 ° and 150 °, for example about 120 ° or about 135 °.

According to another embodiment of the invention, the first angle is about 0 ° and the second angle is about 120 °.

According to another embodiment of the invention, the first angle is about 45 ° and the second angle is about 135 °.

According to an embodiment of the invention, the first predetermined circumferential position and the second predetermined circumferential position are angularly offset with respect to each other.

According to an embodiment of the invention, the first predetermined circumferential position and the second predetermined circumferential position are substantially identical such that the circumferential wall extends over an angle of about 360 °.

According to an embodiment of the invention, the circumferential wall has a thickness and a height configured to ensure a pure elastic deformation of the circumferential wall during operation of the scroll compressor.

According to an embodiment of the present invention, the recess has a depth configured such that the circumferential wall axially overlaps at least a portion of the orbiting scroll support.

According to an embodiment of the invention, the recess is formed by a groove, for example by an annular groove or a semicircular groove.

According to an embodiment of the invention, the recess has a substantially semi-circular disc shape.

According to an embodiment of the invention, the circumferential wall has an upper edge having a tapered shape or a rounded shape.

According to an embodiment of the invention, the vertical drive shaft comprises an oil supply channel configured to be in fluid communication with an oil tank of the scroll compressor, the oil supply channel extending over at least a portion of the length of the vertical drive shaft and having an upper end extending into the axial end face of the crank pin.

According to the embodiment of the present invention, the orbiting scroll supporter is provided in the connection sleeve portion of the orbiting scroll, and the crank pin 21 is inserted in the connection sleeve portion of the orbiting scroll. Advantageously, the connection sleeve portion extends from the driven end plate.

The invention also relates to a vertical drive shaft for a scroll compressor, the vertical drive shaft having a crankpin at an upper end thereof, the crankpin including an outer peripheral surface configured to cooperate with an orbiting scroll support, wherein the crankpin includes a recess formed in an axial end face thereof, the recess and an upper portion of the outer peripheral surface defining a circumferential wall therebetween, the circumferential wall extending along at least a portion of a circumference of the crankpin.

These and other advantages will become apparent upon reading the following description taken in conjunction with the accompanying drawings which illustrate, by way of non-limiting example, an embodiment of a scroll compressor in accordance with the present invention.

Drawings

The following detailed description of several embodiments of the invention will be better understood when read in conjunction with the appended drawings, however, the invention is not limited to the specific embodiments disclosed.

Fig. 1 is a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention.

Fig. 2 is an enlarged view of a detail of fig. 1.

FIG. 3 is a top view of a vertical drive shaft of the scroll compressor of FIG. 1.

Fig. 4 is a cross-sectional view taken along line IV-IV of fig. 3.

FIG. 5 is a top plan view of a vertical drive shaft of a scroll compressor according to a second embodiment of the present invention.

Fig. 6 is a cross-sectional view taken along line VI-VI of fig. 5.

FIG. 7 is a top plan view of a vertical drive shaft of a scroll compressor according to a third embodiment of the present invention.

Fig. 8 is a cross-sectional view taken along line VIII-VIII of fig. 7.

Detailed Description

Fig. 1 shows a scroll compressor 2, the scroll compressor 2 including a hermetic housing 3, the hermetic housing 3 being provided with a suction port 4 configured to supply refrigerant to be compressed to the scroll compressor 2, and with a discharge port 5 configured to discharge compressed refrigerant.

The scroll compressor 2 further includes a support frame 6 and a compression unit 7, the support frame 6 being disposed inside the hermetic case 3 and fixed to the hermetic case 3, and the compression unit 7 also being disposed inside the hermetic case 3 and disposed above the support frame 6. The compression unit 7 is configured to compress refrigerant supplied from the suction port 4, and the compression unit 7 includes a fixed scroll 8 and an orbiting scroll 9 fitted to each other. Specifically, the orbiting scroll 9 is supported by and in sliding contact with the upper surface of the support frame 6, and the fixed scroll 8 is fixed with respect to the hermetic case 3.

The fixed scroll 8 has a fixed end plate 11, and a fixed spiral wrap 12 projecting from the fixed end plate 11 toward the orbiting scroll 9. The orbiting scroll 9 has an orbiting spiral wrap 14 in which first faces of an orbiting end plate 13 and a driven end plate 13 protrude toward the fixed scroll 8. An orbiting spiral wrap 14 of the orbiting scroll 9 is engaged with a stationary spiral wrap 12 of the stationary scroll 8 to form a plurality of compression chambers 15 between the orbiting spiral wrap 14 and the stationary spiral wrap 12. The compression chamber 15 has a variable volume that decreases from the outside inward as the orbiting scroll 9 orbits relative to the fixed scroll 8.

The scroll compressor 2 also includes a motor 16 disposed below the support bracket 6. The motor 16 has a rotor 17 and a stator 18 disposed around the rotor 17.

Further, the scroll compressor 2 includes a vertical drive shaft 19, the vertical drive shaft 19 being connected to the rotor 17 of the motor 16 and configured to drive the orbiting scroll 9 about an orbital motion (orbital).

The vertical drive shaft 19 includes a crank pin 21 at an upper end portion of the vertical drive shaft 19, the crank pin 21 being eccentric with respect to the rotational axis a of the vertical drive shaft 19 and inserted into a connecting sleeve portion 22 of the orbiting scroll 9 so that the orbiting scroll 9 is driven to orbit with respect to the fixed scroll 8 when the motor 16 is operated. The connecting sleeve portion 22 protrudes in particular from the second face of the driven end plate 13.

Crank pin 21 includes an outer peripheral surface 23, which outer peripheral surface 23 cooperates with an orbiting scroll bearing 24 mounted within a connecting sleeve portion 22 of orbiting scroll 9.

The crank pin 21 further includes a recess 25 formed in an axial end surface 26 of the crank pin 21 and radially offset from the outer peripheral surface 23 of the crank pin 21. In other words, the recess 25 does not appear in the outer circumferential surface 23. This configuration of the recess 25 ensures that the outer peripheral surface 23 of the crank pin 21, which cooperates with the orbiting scroll support 24, is retained. According to a first embodiment of the invention, shown in fig. 1 to 4, the recess 25 is formed by an annular circumferential groove.

Advantageously, between the recess 25 and the upper portion 27 of the outer peripheral surface 23 a circumferential wall 28 is defined, which circumferential wall 28 has a curved shape and extends along at least a portion of the circumference of the crank pin 21. According to the first embodiment of the invention shown in fig. 1 to 4, the circumferential wall 28 has an annular shape and extends along the entire circumference of the crank pin 21. Advantageously, the circumferential wall 28 has a constant thickness along its periphery.

The circumferential wall 28 includes an outer circumferential wall surface 28.1 defined by the outer circumferential surface 23 of the crank pin 21 and an inner circumferential wall surface 28.2 parallel to the outer circumferential wall surface 28.1. According to the first embodiment of the invention shown in fig. 1 to 4, the outer circumferential wall surface 28.1 and the inner circumferential wall surface 28.2 are centered on the crank pin axis B and are cylindrical. However, according to another embodiment of the invention, the inner circumferential wall surface may diverge from the bottom surface 25.1 of the recess 25 towards the axial end face 26 of the crank pin 21.

The circumferential wall 28 has an upper edge 29, which upper edge 29 may have a tapered or rounded shape.

In particular, the circumferential wall 28 extends in particular in a region 30 in which region 30 the bearing load F exerted on the outer peripheral surface 23 of the crank pin 21 is greatest. Advantageously, the circumferential wall 28 has a thickness and height configured to ensure pure elastic deformation of the circumferential wall 28 during operation of the scroll compressor 2, and the recess 25 has a depth configured such that the circumferential wall 28 axially overlaps at least a portion of the orbiting scroll support 24.

Due to this configuration of the circumferential wall 28, when the orbiting scroll 9 performs a tilting or oscillating movement, the circumferential wall 28 may be deformed in the radial direction, particularly in the region 30 where the bearing load F applied to the outer peripheral surface 23 of the crank pin 21 is maximum.

Therefore, during the operation of the scroll compressor 2, the contact pressure between the orbiting scroll support 24 and the outer peripheral surface 23 of the crank pin 21 is significantly reduced, which increases the life of the orbiting scroll support 24.

The vertical drive shaft 19 also includes an oil supply passage 31, the oil supply passage 31 being configured to be in fluid communication with an oil tank 32 of the scroll compressor 2. In particular, the oil supply channel 31 extends over the entire length of the vertical drive shaft 19 and its upper end extends into the axial end face 26 of the crank pin 21.

Fig. 5 and 6 show a vertical drive shaft 19 of a scroll compressor 2 according to a second embodiment of the present invention which differs from the scroll compressor 2 of fig. 1 to 4 mainly in that the recess 25 is formed by a semicircular recess, and the circumferential wall 28 has an arcuate shape and extends only along a part of the circumference of the crank pin 21.

In particular, the circumferential wall 28 extends at an angle of about 180 ° centered on the crankpin axis in the region 30 where the bearing load F applied to the outer circumferential surface 23 of the crankpin 21 is greatest and between the first predetermined circumferential position P1 and the second predetermined circumferential position P2.

According to the second embodiment of the invention, the first predetermined circumferential position P1 is located in a first half space defined by a reference plane P including the crank pin axis B and the rotation axis a of the vertical drive shaft 19, and the second predetermined circumferential position P2 is located in a second half space defined by the reference plane P.

A first orthogonal projection of the first predetermined circumferential position P1 in a projection plane orthogonal to the crank pin axis B and to the axis of rotation a of the vertical drive shaft 19 and a reference half-line, which comprises an initial point corresponding to the orthogonal projection of the crank pin axis B in the projection plane and passes through a reference point corresponding to the orthogonal projection of the axis of rotation a of the vertical drive shaft 19 in the projection plane, define a first angle α, which is centered on said initial point and is approximately 45 °, which is measured from the reference half-line in a first measuring direction.

Advantageously, a second orthogonal projection of the reference half-line and the second predetermined circumferential position P2 in the projection plane defines a second angle β, centered on said initial point and about 135 °, measured from the reference half-line in a second measurement direction opposite to the first measurement direction. According to another embodiment of the present invention, the first angle α may be about 0 ° and the second angle β may be about 120 °.

Fig. 7 and 8 show a vertical drive shaft 19 of a scroll compressor 2 according to a third embodiment of the present invention, which differs from the scroll compressor 2 of fig. 5 and 6 mainly in that the recess 25 has a semicircular disk shape.

The invention is of course not limited to the embodiments described above by way of non-limiting examples, but on the contrary encompasses all embodiments.