JPS60119388A - Horizontal oil pump - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to oil pumps, and in particular to oil pumps for use in horizontal rotary compressors.

In some compressors, the crankshaft 7) is arranged vertically within the compressor housing, with the lower end of the crankshaft immersed in an oil sump. The crankshaft is provided with a spiral groove, and when the crankshaft is rotated by an electric motor, oil is sent upward to the crankshaft by miso.
It lubricates bearings and other moving parts. Typically, the lower end of the crankshaft also includes some type of propulsion means to force oil upwardly through the helical groove.

In contrast to the compressors described above, in which oil is pumped upward through a spiral groove on the vertically mounted crankshaft, horizontal piston compressors or horizontal rotary compressors pump oil upward through a spiral groove in the crankcase. cannot be raised directly. This has created many problems in properly lubricating the bearings and other moving parts within the horizontally arranged conrussor. Although the prior art horizontal compressors currently in use employ some means of delivering lubricant to the rotating horizontal crankshaft, it is still necessary to adequately lubricate the bearings and other moving parts. Problems persist, including the inability to provide sufficient self-priming (5) and water to the oil pump during start-up.

An early method of delivering lubricant upwardly to a rotating horizontal crankshaft was to attach a disk to the crankshaft, rotate it in unison, and place the lower portion of the disk in a sump.

A circular miso is provided on the plane of the disc, and when the disc rotates through the oil pool, the lubricant is carried upwards by the grooves.
It enters a cavity or chamber adjacent to the crankshaft.

The lubricant is then conveyed from the chamber to the crankshaft by a series of passages to lubricate the bearings. This type of oil pump is associated with some deficiencies, one of which is the inability to deliver the desired amount of lubricant to the crankshaft and attached bearings. Other deficiencies include the added expense of materials and labor to provide the chamfer disc and chamber with oil passages to the crankshaft and bearings in the crankcase.

Another type of oil pump used with horizontal electric compressor units uses a wick device located in the oil sump (6) and in contact with the crankshaft at some axial point. The wick device delivers oil upwardly from the oil sump, and the oil travels through the wick to the crankshaft and is delivered to the crankshaft and bearings. The obvious drawback of this type of lubrication device is that over long-term use, the wick shrinks and falls off the crankshaft, so that the crankshaft and bearings are no longer properly lubricated. Furthermore, the wick eventually becomes shredded into small pieces that can block oil passages or get between moving parts, impeding proper movement.

In yet another type of horizontal compressor, a portion of the crankcase is immersed in the oil sump, and a portion of the crankcase is immersed in the oil sump and extends upwardly from the oil sump and is located between the eccentrically reduced portion of the crankshaft and the crankcase. It has a passageway leading up to the room.

As the crankshaft rotates, oil is drawn upwardly through this crankcase passage into the chamber and into a passage extending axially within the crankshaft. One of the deficiencies with this particular type of oil pump is that
The axially extending passages leading into the chambers do not take full advantage of the centrifugal force of the rotating crankshaft, thereby efficiently delivering the desired amount of lubricant along the crankshaft to lubricate the bearings. This means that they should not be paid.

Yet another type of oil pump system for rotating horizontal shafts has a large center portion of the shaft with cheekbones extending axially inward toward each end. The enlarged central portion is provided with a pair of oppositely angled spirals on each plane, the outermost axial ends of which communicate with the oil supply. As the shaft and the spiral shaft on the shaft rotate, oil is pumped axially inward along the shaft to reach and lubricate the center of the shaft.

One undesirable feature of this type of oil pump is the need to arrange the oil supply in the same haze as both ends of the rotating horizontal shaft. In virtually all horizontal rotating compressors, the crankshaft!・ is located above the surface of the oil sump in the conrussa housing.

In view of the above, the oil pump in the horizontal compressor unit is designed to efficiently deliver lubricant upward to the crankshaft and horizontally along the length of the crankshaft to support bearings and other moving parts. properly lubricated,
It is also very clear that there is still a desire to be able to self-prime.

In the horizontal shaft oil pump of the present invention, any type of disc or wick device is not used to deliver lubricant upward to the crankshaft, but instead is located within the oil sump. A roughly vertical passage is provided in a part of the crankcase.

This passage leads to the oil sump and extends upwards to the crankshaft. The diameter of a portion of the crankshaft is reduced to form an annular chamber between the crankshaft raceway and the crankcase that communicates with the crankcase passage.

When the crankshaft rotates, a low pressure area is created in this annular chamber, and the lubricant is drawn upwards from the oil sump through the crankcase passage and reaches the annular chamber (9).

The horizontal shaft oil pump of the present invention accomplishes what many prior art oil pumps cannot do by delivering the amount of lubricant necessary to lubricate the bearings and other moving parts to the horizontal crankshaft. Supply efficiently. The above ``what could not be done'' is that a pair of spiral grooves oriented in opposite directions are provided on both sides of the annular chamber, and these grooves create an annular chamber between the crankshaft and the crankcase. The solution is to form a pair of oppositely oriented helical passages that communicate and proceed away from this chamber. These spiral passages are arranged in opposite directions to convey oil from the annular chamber in opposite directions. As the horizontal crankshaft rotates, an area of low pressure that develops within the annular chamber draws lubricant from the oil sump through the crankcase passageway and into the annular chamber. The lubricant is then fed along the crankshaft by each helical groove to lubricate the bearings and other moving parts.

The dimensions of each helical groove are such that sufficient oil flow is obtained to adequately lubricate the bearings (lO) and to allow the pump to self-prime upon start-up.

In one form of the invention, a compressor is provided with a housing having one inlet, one outlet, and a sump at the bottom. A motor-compressor unit is mounted within the housing and includes a crankcase having a generally vertical passage leading to an oil sump, a rotatable crankshaft, and means for compressing refrigerant. The crankshaft is generally horizontally arranged and rotatably received within the crankcase. The crankshaft also has a reduced diameter portion forming an annular chamber between the crankshaft and the crankcase that communicates with the crankcase passage. Furthermore, the crankshaft also includes a helical shaft between the crankshaft and the crankcase, forming a helical passage between the annular chamber and the compression means. As the crankshaft rotates, a low pressure region is created within the annular chamber that draws lubricant upward through the crankcase passageway and into the annular chamber. This oil is then fed axially along the crankshaft by a helical passage to lubricate the crankshaft bearings.

It is an object of the present invention to provide an improved horizontal shaft oil which draws a desired amount of lubricant upwardly from a sump and efficiently delivers it cleanly and horizontally to a crankshaft to lubricate bearings and other moving parts. is to provide a pump.

Another object of the invention is to provide an improved horizontal shaft oil pump that is self-priming.

Yet another object of the invention is to provide an improved horizontal shaft oil pump that is inexpensive to manufacture and easy to assemble.

Other objects of the invention will become apparent as the description progresses.

The present invention will be described in detail below with reference to the accompanying drawings.
From this description, the above and other features and objects of the invention,
As well as how to achieve them, it will become clearer and the invention itself will be better understood.

Now, FIGS. 1 and 2 show a rotary compressor 10 incorporating a horizontal shaft oil pump 11 according to the present invention.
is shown. The present invention will be described below with respect to the rotary compressor 10, but the horizontal shaft oil cylinder 7D11
It can also be incorporated into other types of compressors that require lubrication of the rotating horizontal shaft.

The electric motor/core compressor unit 8 of the rotary compressor 10 includes a rotor 15 and a stator 1 having a winding 16.
4 and a cylindrical housing 12 shrink-fitted onto a stator 14. Both ends of the housing 12 have end plates 1812 welded to the housing.
Closed by 0. The end plate 12 includes a terminal pin assembly 22 and a spout 24 to which a spout tube 26 is connected by a connector 28 .

The end plate 20 has an opening 30 for passing a suction inlet pipe 32 therethrough.
Contains. A pair of mounting brackets 34 are welded to opposite ends of the housing 120, each bracket including a pair of retaining members such as (13) resilient grommets (36, 38).

A crankcase 42 is mounted within the interior 40 of the housing 12, and the crankcase 42 includes a main bearing assembly having oil passages 46 arranged generally vertically therein.
Contains 44. The housing 12 includes an oil sump 48 , and the lower part of the main bearing block 44 is immersed in the oil sump 48 so that the oil sump 48 is horizontally distributed within the crankcase 42 through an oil passage 46 . cavity 5
It leads to 0. For the purposes of this application, the term "vertically oriented" as used in the passageways 46 is used in a broad sense to mean that oil flows upwardly from the sump 48 against the force of gravity. are doing.

A crankcase interior 52 is horizontally and rotatably received within bore 50. The rotor 15 is shrink fit onto a portion 54 (see FIGS. 3, 4, and 7) of a crankshaft 52, and when current is supplied to the motor 13 through the terminal pin assembly 22, the crankshaft 52 (14).

The opposite end of crankshaft 52 includes an eccentric member 58 having a groove 59 and is received within a cylinder plate 60 that is connected to main bearing block 44 by screws 66 . A roller 62 is rotatably received about eccentric member 58 within cylinder 60 and a valve plate or backing plate 64 is attached to cylinder 60 by screws 66. The discharge muffler 68 is attached to the back plate 6 by the screw 66.
4, and the back plate 64 is attached to the crankshaft 5.
2 and a hole 70 that is axially aligned with the open lower portion 2 in the muffler 68 . A vane 63 is slidably received in a groove 67 in the cylinder plate 60 and biased toward the roller 62 by a C-shaped spring 65 secured to the cylinder plate 60. cylinder plate 6
0 has an inlet 69 into which the suction inlet pipe 32 leads.

Valve assembly 74 is adapted to compress refrigerant flowing from cylinder 60 through back plate 64 and into discharge muffler 68 . Valve assembly 74 includes an opening arrow in back plate 64 that communicates between cylinders 60 and 77 and 68 . The leaf spring 78 is screwed into the valve retainer 80 and through the valve retainer 80 and the valve into the back plate 64 by screws 82 (FIG. 2).
It is fixed in a predetermined position on the opening arrow by.

Reference is now made to FIGS. 1 and 3 to 6.

The crankshaft 52 has a reduced diameter 1. central part 8
4, and this portion 84 is located inside the crankcase 52.
An annular chamber 86 communicating with the oil passage 46 is formed between the crank case 42 and the crank case 42 . The crankshaft 52 has
Both sides of this annular chamber 86 communicate with this chamber 86 .

A pair of helical grooves 88.90 are provided.

As shown in FIGS. 3 and 4, grooves 88 and 90 are oppositely oriented within crankshaft 52 to direct lubricant from annular chamber 86 to crankshaft 52 in both directions. It looks like this. Each groove 88,90
The radial dimension or depth and axial dimension or length of
It is predetermined as a function of several variables, such as the diameter and length of the crankshaft, and the vertical height of the crankshaft from the sump. Grooves 88 and 90 form raised portions 92
The crankshaft 52 is machined to provide a sufficient bearing surface between the N50 and the inner surface of the crankcase N50, and at the same time to efficiently supply the desired amount of lubricant along the crankshaft 52. ing. In this embodiment, as shown in FIG. 6, each groove 88, 90 has a bottom surface 94 and a raised portion 9 from the bottom surface 94 for ease of machining.
96.98 and radially outwardly extending and upwardly extending sides 96,98.

The numerical values set forth below are dimensions of a typical working embodiment of a crankshaft 52 according to the present invention, but they are for illustrative purposes only and are not intended to limit the scope of the present invention.

Compressor horsepower: 1/4 (17) Crankshaft axial length: 85.852~85
．． 979+nm (de-eccentric member 5B) (3,380~3
．． 385 inches) Side angle of 96.98: 43°~
47° grooves 88.90 are machined into the crankshaft 52 at 4 grooves per inch, forming a 100° helical passage between the crankshaft 52 and the crankcase 42 leading to an annular chamber 86, as shown in FIG. 102 is formed. Passage 102 also communicates with groove 59 (FIG. 4) in eccentric member 58.

The operation will be explained. When current is supplied from terminal pin assembly 22, rotor 15 and crankshaft 52 rotate, and refrigerant flows from suction inlet pipe 32 and inlet 69 into cylinder 6.
Supplied within 0. When the crankshaft 52 rotates, the eccentric member 58 causes the p-ra 62 to rotate within the cylinder 60, compressing the supplied refrigerant. The compressed refrigerant is discharged through valve assembly (18) 74 into muffler 68 and then into the interior 40 of housing 12 through an opening (not shown) in muffler 68. The compressed refrigerant passes over motor 13 to cool motor 13 and is then discharged through outlet 24 into discharge pipe 26 .

Please refer to FIGS. 1, 4 and 7. As soon as the crankshaft 52 rotates, lubrication occurs. As crankshaft 52 rotates, a localized vacuum or low pressure region is created within annular chamber 86 , drawing lubricant from oil sump 48 through oil passageway 46 and into chamber 86 . Lubricant is delivered in both directions from the annular chamber 86 by a helical passageway 100° 102. The lubricant is discharged from the helical passageway 100 onto the rotor 15, which injects the lubricant outwardly toward the inner surface of the housing 12 to cool it and fill the oil sump 4.
Return to 8.

The lubricant delivered by the helical passageway 102 lubricates the bore 50 of the crankcase 42 and the groove 5 of the eccentric member 58.
9 and exits from passage 102. The lubricant delivered to groove 59 lubricates the surfaces of eccentric member 58 and roller 62, which are engaged with each other. The lubricant then passes through the groove 59, the hole 70 in the back plate 64, and the open lower portion 2 of the discharge muffler 68, and returns to the oil sump 48.

If desired, external bearings (not shown) may be provided on the eccentric member 58 to rotate within the hole 70 in the back plate 64. Such an external bearing is provided with an oil passage communicating with the groove 59 of the eccentric member 58 so that lubricant is fed through the external bearing and returned to the oil reservoir 48.

Although preferred embodiments of the invention have been described above, it will be understood that many modifications are possible. It is therefore to be understood that the invention covers any variations, uses or adaptations thereof based on its general principles.

[Brief explanation of drawings]

1 is a longitudinal cross-sectional view of a preferred embodiment of the present invention, FIG. 2 is a partially omitted end view of the embodiment of FIG. 1, and FIG. 3 is a crank of the embodiment of FIG. 1. 4 is a plan view of the crankshaft of FIG. 3; FIG. 5 is an end view of the crankshaft of FIG. 4; and FIG. 6 is a side view of the crankshaft of FIG. 3. 7 is a partially omitted cross-sectional view of the spiral, and FIG. 7 is a partially omitted perspective view of the embodiment of FIG. 1 to show the flow of lubricant. 8... Electric motor/congressor unit, 10... Rotary compressor, 11... Horizontal shaft oil pump, 12... Housing, 13... Electric motor, 14...
- Stator, 15... Rotor, 16... Winding wire, 18.
20... End plate, 22... Terminal/bin assembly, 24...
...Discharge port, 26...Discharge pipe, 28...Connector,
30...Opening, 32...Suction inlet pipe, 34...Bracket for mounting, 36.38...Grommet, 40
... Inside the housing, 42 ... Crank case, 4
4... Main bearing block, 46... Oil passage, 48...
- Oil reservoir, 50... Inner cavity, 52 (21)... Crankshaft 7), 54... Part of crankshaft, 58... Eccentric member, 59... Groove, 60...
... Cylinder plate, 62 ... Roller, 63 ... Vane,
64... Back plate, 65... C-shaped spring, 66... Screw, 67... Groove, 68... Discharge muffler, 69...
... Entrance, 70... Hole, 72... Opening, 74...
Leaf spring, 80... Valve retainer, 82... Screw, 84...
... Central portion of the crankshaft, 86... Annular chamber, 88, 90... Spiral groove, 92... Raised portion,
94...bottom, 96.98...side, 100110
2...Spiral passage. (22) JP-A-Sho GO-119388 (7) FIG-3FIG-6 FIG-4FIG-5 IG-7

Claims (1)

[Claims] 1. An oil reservoir (
a housing (12) having (48) and a crankcase (42), oil passages (46) arranged approximately vertically and communicating with said oil sump, a rotatable rank shaft (52), a cylinder (60); , and an electric motor/conzoresor unit (8) connected to the crankshaft and including means for compressing refrigerant and mounted within the housing: the crankshaft is arranged in a generally horizontal arrangement; is rotatably received within said crankcase and is reduced in diameter to form an annular chamber (86) between said crankshaft and said crankcase communicating with said oil passageway. said crankshaft includes a helical groove (90), said helical groove defining said annular chamber and said compression means between said crankshaft and said crankcase; A spiral passageway (102) is formed between the crankshaft and the annular chamber, so that when the crankshaft rotates, a low-pressure region is generated in the annular chamber, and the lubricant is drawn upward through the oil passage and into the annular chamber. wherein the helical passageway in the crankshaft during rotation is configured to flow lubricant from the annular chamber to the crankshaft to lubricate the bearings. electric compressor. 2. The crankshaft has a second helical groove (88
), the second spiral passage communicating with the annular chamber between the crankshaft and the crankcase and extending from the annular chamber in a direction opposite to the first helical passageway. a second helical passageway (ioo) is formed, the second helical passageway (ioo) being oriented inversely to the first helical passageway within the crankshaft to direct lubricant from the chamber to the first passageway; 2. The compressor according to claim 1, wherein the compressor is configured to lubricate other bearings by feeding in a direction opposite to that of the compressor. 3. Both sides facing each other (96, 98)
3. The compressor according to claim 2, wherein the compressor expands outward in a radial direction. 4. The compressor according to claim 3, wherein the radial dimension of each of the compressors is smaller than the axial dimension. 5. said compression means are rotary compression means comprising an eccentric member (58) and an annular roller member (62) rotatably received around said member; A groove (59) communicating with the spiral passageway and extending in the axial direction is provided on the outer surface thereof to feed lubricant between the eccentric member and the roller member. A compressor according to claim 1. 6. The crankshaft has a second helical groove (88
), the second helical passage communicating with the annular chamber between the crankshaft and the crankcase and extending from the annular chamber in a direction opposite to the first helical passage. a second helical passageway (100), said second helical passageway being arranged inversely to said first helical passageway for transporting lubricant from said annular chamber to the opposite end of said crankshaft; Claim 5 characterized in that the lubricant is supplied to the other bearings to lubricate the other bearings.
Compressor described in. 7. The radial dimension of the side groove is smaller than the axial dimension of the side groove, and each of the opposing side surfaces (96, 98) of each groove is radially outward from the bottom surface thereof. The compressor according to claim 6, characterized in that it is wide.