Compressor Piston Shape to Reduce Clearance Volume

Abstract

A piston assembly for reducing clearance volume in a reciprocating compressor for compensating for piston tilt and improving the volumetric efficiency of the compressor includes a piston located within a piston cylinder, the piston having a first end and a second end, a wrist pin associated with the first end of the piston, and a cylinder head/valve assembly associated with the second end of the piston, wherein at least a portion of the second end of the piston includes an angled portion. The piston having the angled portion can be used with oil free cylinders and trunk type pistons. The piston can also be used in a multiple stage, multiple cylinder compressor including a series of piston assemblies. A method of increasing the volumetric efficiency of a reciprocating compressor can also be achieved using the piston having an angled portion.

Claims

1. A piston assembly for use with a reciprocating compressor comprising: a piston located within a piston cylinder, said piston having a first end and a second end; a wrist pin associated with the first end of the piston; a cylinder head/valve assembly associated with the second end of the piston, wherein at least a portion of the second end of the piston includes an angled portion.

2. The piston assembly of claim 1, wherein at least a portion of the angled portion of the second end of the piston and the cylinder head/valve assembly define a clearance volume.

3. The piston assembly of claim 2, wherein the angled portion is shaped to compensate for tilt of the piston after a top dead center of the piston is reached during a reciprocating cycle of the piston.

4. The piston assembly of claim 1, wherein the wrist pin is configured to receive the first end of the piston so that the angled portion extends in a spaced orientation relative to the cylinder head/valve assembly to accommodate tilt of the piston.

5. The piston assembly of claim 1, wherein the angled portion includes a slope extending in a downward direction from a center portion of the piston toward an outer edge portion of the piston.

6. The piston assembly of claim 1, wherein the second end of the piston includes two angled portions.

7. The piston assembly of claim 6, wherein each of the angled portions include a slope extending in a downward direction, at opposite locations from each other, and extending from a center portion of the piston toward opposed outer edge portions of the piston.

8. The piston assembly of claim 1, wherein the wrist pin includes a connecting rod and a crankshaft.

9. The piston assembly of claim 1, wherein the pistons are configured for use with oil free cylinders and trunk type pistons.

10. A multiple stage, multiple cylinder compressor including a series of piston assemblies, each of the piston assemblies comprising: a piston located within a piston cylinder, said piston having a first end and a second end; a wrist pin associated with the first end of the piston cylinder; and a cylinder head/valve assembly associated with the second end of the piston, wherein at least a portion of the second end of the piston includes an angled portion.

11. The piston assembly of claim 10, wherein at least a portion of the angled portion of the second end of the piston and the cylinder head/valve assembly define a clearance volume.

12. The piston assembly of claim 11, wherein the angled portion is shaped to compensate for tilt of the piston after a top dead center of the piston is reached during a reciprocating cycle of the piston.

13. The piston assembly of claim 10, wherein the wrist pin is configured to receive the first end of the piston so that the angled portion extends in a correct orientation with respect to the cylinder head/valve assembly.

14. The piston assembly of claim 10, wherein the angled portion includes a slope extending in a downward direction from a center portion of the piston toward an outer edge portion of the piston.

15. The piston assembly of claim 10, wherein the second end of the piston includes two angled portions.

16. The piston assembly of claim 15, wherein each of the angled portions include a slope extending in a downward direction, at opposite locations from each other, and extending from a center portion of the piston toward opposed outer edge portions of the piston.

17. The piston assembly of claim 10, wherein the wrist pin includes a connecting rod and a crankshaft.

18. A method of increasing the volumetric efficiency of a reciprocating compressor comprising: providing a piston assembly configured for use with the reciprocating compressor, said piston assembly including a piston located within a piston cylinder, said piston having a first end and a second end; a wrist pin associated with the first end of the piston cylinder; and a cylinder head/valve assembly associated with the second end of the piston; and providing an angled portion on at least a portion of the second end of the piston.

19. The method of claim 18, including providing the angled portion with a slope extending in a downward direction from a center portion of the piston toward an outer edge portion of the piston.

20. The method of claim 18, including providing two opposed angled portions on the second end of the piston.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0022] FIG. 1 is a cross-sectional side view of a piston in accordance with the prior art at the top dead center just prior to changing directions.

[0023] FIG. 1A is an exploded view of section 1A of FIG. 1 showing the clearance volume between the piston and cylinder head/valve.

[0024] FIG. 1B is an exaggerated view of the piston and the bottom portion of the valve of FIG. 1 showing the clearance volume therebetween before tilting the piston.

[0025] FIG. 2 is a cross-sectional side view of the piston of FIG. 1 in a tilted position.

[0026] FIG. 2A is an exploded view of section 2A of FIG. 2 showing the increased clearance distance between the piston and cylinder head/valve caused by titling in accordance with the prior art.

[0027] FIG. 2B is an exploded view of section 2B of FIG. 2 showing the decreased clearance distance between the piston and cylinder head/valve caused by tilting.

[0028] FIG. 2C is an exaggerated view of the piston and the bottom portion of the valve of FIG. 2 after tilting of the piston.

[0029] FIG. 3 is a cross-sectional view of a known piston and cylinder in which additional clearance is provided between the piston and cylinder.

[0030] FIG. 3A is an exaggerated view of the piston and valve of FIG. 3 before titling of the piston.

[0031] FIG. 3B is an exaggerated view of the piston and valve of FIG. 3 after tilting of the piston.

[0032] FIG. 4 is a top view of a piston with an angled portion in accordance with the principles of this disclosure.

[0033] FIG. 5 shows a cross-sectional side view of a piston and cylinder wherein the piston includes an angled portion as shown in FIG. 4.

[0034] FIG. 5A is an exaggerated view of the piston and valve of FIG. 5 before titling of the piston.

[0035] FIG. 5B is an exaggerated view of the piston and valve of FIG. 5 after tilting of the piston.

DESCRIPTION OF THE INVENTION

[0036] For purposes of the description hereinafter, spatial orientation terms, as used, shall relate to the referenced embodiment as it is oriented in the accompanying drawing figures or otherwise described in the following detailed description. However, it is to be understood that the embodiments described hereinafter may assume many alternative variations and configurations. It is also to be understood that the specific components, devices, and features illustrated in the accompanying drawing figures and described herein are simply exemplary and should not be considered as limiting.

[0037] Referring to FIGS. 1-5, a piston assembly, generally designated 10, is shown for use with a reciprocating compressor for maximizing the volumetric efficiency of the compressor. Normally, a pneumatic system is provided for a rail vehicle by which the brakes of the rail vehicle are operated. An air compressor is used to supply compressed air to one or more pneumatic units associated with the rail vehicle involved in the operation of the brakes. The air compressor usually consists of a driving unit, such as an electric motor, and of a compressor unit, which typically consists of several piston-cylinder assemblies 10 that are driven by a crankshaft.

[0038] With continuing reference to FIGS. 1 and 2, the piston assembly 10 includes a piston 12, having one or more piston rings 13 located within a piston cylinder 14. The piston 12 has a first end 16 and a second end 18. A wrist pin 20 is associated with the first end 16 of the piston 12. The wrist pin 20 is connected to one end 24 of a connecting rod 22. The opposite end 26 of the connecting rod 22 is connected to a crankshaft (not shown) which directly drives the piston 12. The piston assembly 10 further includes a cylinder head 28 and valve 30 associated with the second end 18 of the piston 12. The cylinder head 28 includes a low side suction line 32 which cooperates with a suction valve 34 in the valve 30 and a high side discharge line 36, which cooperates with a discharge valve 38 in the valve 30, which cooperate together to give the compressor the ability to pump air against a pressure difference.

[0039] During a complete revolution of the crankshaft, as the crankshaft rotates, the piston 12 begins to move downward, reducing the pressure in the piston cylinder 14. This reduced pressure causes the suction valve 34 to open and allow air to flow from the low side suction line 32 and into the piston cylinder 14 until the piston cylinder 14 is filled with air and the piston 12 is at the bottom of its stroke or at bottom dead center. As the crankshaft continues to rotate and cause the piston 12 to begin its upward stroke, the suction valve 34 closes. As the piston 12 continues to move in an upward direction, the volume within the space of the piston cylinder 14 reduces, increasing the pressure of the air. This increased pressure causes the discharge valve 38 to open, letting the compressed air flow out of the piston cylinder 14 and through the high side discharge line 36 until the piston 12 reaches the top dead center position, as shown in FIG. 1.

[0040] As discussed above, the volumetric efficiency of a reciprocating compressor is defined by the ratio of the actual amount of air flow discharged from the compressor (actual air delivery volume) to the total amount of air that can theoretically flow into the compressor inlet during the intake stroke (swept volume). The actual amount of compressed air delivered from the compressor can be effected by the amount of volume between the top 12a of the piston 12 (the crown) and the cylinder valves 34, 38 when the piston 12 is at the top of its stoke or top dead center. This volume is called the clearance volume 40, as shown illustrated in FIGS. 1A and 1B. The clearance volume 40 defines the amount of air that is pulled into the cylinder on the intake stroke, compressed during the compression stroke, but is not discharged from the cylinder before the next intake stroke.

[0041] During operation of the piston assembly 10, the compressed air left behind in the clearance volume 40 re-expands filling the cylinder volume that otherwise would have been filled with atmospheric air being pulled into the piston cylinder 12. The end result of the re-expansion is that the piston assembly 10 is not capable of delivering, during the discharge stroke, the same amount of air that can be theoretically ingested into the piston assembly 10 during the intake stroke.

[0042] With continuing reference to FIG. 1, a piston 12 is shown at its top dead center just prior to changing directions. FIGS. 1A and 1B show the clearance volume 40 between the piston 12 and the valve 30. As illustrated in FIG. 2, when the piston 12 changes direction, especially during unloaded operation, the piston 12 tilts in the piston cylinder 14 about the wrist pin 20, which acts as a fulcrum. This tilt is illustrated in FIG. 2 showing the piston 12 at the moment just after the top dead center position. The piston tilt causes the distance between the top 12a of the piston 12 and the cylinder head 28 and valve 30 to increase on one side, as indicated at 42 in FIGS. 2A and 2C, and to decrease on the other side, as indicated at 44 in FIGS. 2B and 2C. If the clearance between the piston and cylinder head 28 and valve 30 is designed to be a minimum when the piston 12 is perpendicular in the bore 15 of the piston cylinder 14, then the clearance between the piston 12 and the cylinder head 28 and valve 30 may reduce to zero when the piston tilts as shown by 44 in FIG. 2B. If the clearance reduces to zero, contact between the piston 12 and the cylinder head 28 and valve 30, as indicated by 31 in FIG. 2C, will eventually, if not immediately, result in compressor failure.

[0043] To account for this piston tilt, a commonly used method is to add extra clearance as shown by 48 in FIGS. 3 and 3A between the piston 12 and the cylinder head 28 and valve 30 at the top dead center. As shown by 43 in FIG. 3B, after tilting, the extra clearance 48 between the piston 12 and valve 30 is sufficient to prevent any contact between the piston 12 and valve 30. While this extra clearance 48 is effective in eliminating the contact, this increased clearance results in increased clearance volume and therefore, reduced compressor efficiency.

[0044] The present disclosure accounts for piston tilt without increasing the clearance volume by providing at least a portion of the second end 18 of the piston 12 with an angled portion 50, as illustrated in FIGS. 4-5. This angled portion 50 of piston 12, shown as 0 in FIGS. 5 and 5A, is sized so that when the piston 12 tilts at the top of the stroke during the change in piston direction within the piston cylinder 14, the additional clearance volume necessary for an oil free compressor does not need to be added across the entirety of the piston 12. As shown in FIGS. 5 and 5A, this angled portion 50 of the second end 18 of the piston 12 defines a clearance volume 40 that is sufficient to compensate for tilt of the piston 12 after a top dead center of the piston 12 is reached during a reciprocating cycle of the piston 12. The wrist pin 20 can be configured to receive the first end 16 of the piston 12 so that the angled portion 50 extends in a correct orientation with respect to the cylinder head 28 and valve assembly 30. As shown in FIGS. 4, 5, and 5A, the angled portion 50 includes a slope extending in a downward direction from the side of a center portion 52 of the piston 12 toward an outer edge portion 54 of the piston 12. According to one design, the center portion 52 is flat and the slope or angled portion 50, as depicted in FIGS. 5 and 5A, starts just to the right of the flat portion 52 and extends away from the top of the piston 12. As shown by 41 in FIG. 5B, after tilting, the angled portion 50 ensures that no contact occurs between the piston 12 and the valve 30.

[0045] According to one embodiment (not shown), the second end 18 of the piston 12 can include two angled portions 50. Each of the angled portions 50 can include a slope extending in a downward direction at opposite locations from each other from the flat center portion 52 of the piston 12 toward opposed outer edge portions 54 of the piston 12.

[0046] According to one embodiment, the piston 12 of the invention can be configured for use with oil free cylinders and trunk type pistons.

[0047] This same phenomenon of volumetric efficiency loss occurs within each stage of a multiple stage compressor. The difference is that the inlet air is at a higher pressure than ambient pressure if the piston assembly 10 is part of the second, third, or subsequent stage of a compressor. The clearance volumes 40 in each piston assembly 10 and stage are additive and result in a reduction in overall compressor efficiency. The role that the clearance volume 40 plays in determining the overall efficiency of an air compressor makes it a critical characteristic of compressor design. Simply stated, a compressor with less clearance volume 40 is more efficient than a compressor with more clearance volume.

[0048] A method of increasing the volumetric efficiency of a reciprocating compressor according to the present invention includes providing a piston assembly 10 configured for use with the reciprocating compressor, wherein the piston 12 located within the piston cylinder 14 includes an angled portion 50 on at least a portion of the second end 18 of the piston 12 which is located adjacent to the cylinder head 28 and valve 30 assembly. As discussed above, providing this angled portion 50 reduces the clearance volume between the second end 18 of the piston 12 and the cylinder head 28 and valve 30 assembly which compensates for tilt of the piston after a top dead center of the piston is reached during a reciprocating cycle of the piston. The angled portion 50 can be provided with a slope extending in a downward direction from a center portion 52 of the piston 12 toward an outer edge portion 54 of the piston 12. According to one embodiment (not shown), the method can include providing two opposed angled portions 50 on the second end 18 of the piston 12.

[0049] While embodiments of piston assembly for reducing clearance volume in a reciprocating compressor for compensating for piston tilt and improving the volumetric efficiency of the compressor is provided in the foregoing description, those skilled in the art may make modifications and alterations to these embodiments without departing from the scope and spirit of the invention. Accordingly, the foregoing description is intended to be illustrative rather than restrictive.