WO2007092708A1

WO2007092708A1 - Pump using torsional energy from a rotating or non-rotating shaft

Info

Publication number: WO2007092708A1
Application number: PCT/US2007/061332
Authority: WO
Inventors: Roger T. Simpson
Original assignee: Borgwarner Inc
Priority date: 2006-02-03
Filing date: 2007-01-31
Publication date: 2007-08-16

Abstract

A pump in which torsional energy from a shaft is converted to high pressure, actuating the pump. A ring (16) surrounds and is fixedly attached to a housing (1). The rotor (3) connects to a shaft (22) coaxially located within the housing. The housing and the rotor define at least one vane (6) separating a chamber in the housing into an advance (2) and a retard chamber (4). A first return spring (18) is received between the housing and the vane in the advance chamber and a second return spring (17) is received between the housing and the vane in the retard chamber. Inlet passages (19; 20) are present between a supply and the advance chamber and the retard chamber. Each of the passages have at least one inlet check valve (14; 15). Outlet passages (12;13) are present between the advance chamber and an output and the retard chamber and an output. Each of the passages has at least one outlet check valve (5; 7).

Description

PUMP USING TORSIONAL ENERGY FROM A ROTATING OR NON- ROTATING SHAFT

REFERENCE TO RELATED APPLICATIONS

This application claims an invention which was disclosed in Provisional Application Number 60/765,504, filed February 3, 2006, entitled "Pump Using Torsional

Energy From A Rotating Or Non-Rotating Shaft" and Provisional Application Number 60/773,431, filed February 15, 2006, entitled, "Pump Using Torsional Energy From A Rotating Or Non-Rotating Shaft." The benefit under 35 USC §119(e) of the United States provisional application is hereby claimed, and the aforementioned applications are hereby incorporated herein by reference.

BACKGROUND OF THE INVENTION

FTELD OF THE TNVENTTON

The invention pertains to the field of pumps. More particularly, the invention pertains to a pump that uses torsional energy from a rotating shaft to operate.

DESCRIPTION OF RELATED ART

Figure 1 shows a graph of the relationship of the torsional energy of the crankshaft of an 14 engine and second order resonance generated as oscillation of the crankshaft and speed increase. In an 14 engine, the torsional energy of the crankshaft, shown by the dashed line, is high when the crank oscillation is high and the average speed is low. The torsional energy decreases as the average speed increases and the crank oscillation decreases. As the speed of the engine increases, the ends of the crankshaft twist and go into resonance, indicated by the unbroken line as shown in Figure 1. Since the firing frequency occurs twice per crank revolution, a second order resonance occurs as the engine speed increases. In order to prevent the resonance, dampers are added to the crankshaft. One type of damper splits the crank resonance shown by the unbroken line of Figure 2 into two lower frequencies, indicated by the dash-dot line, that are opposite of the crank resonance.

Another type of damper used to prevent resonance is a friction damper. By creating friction between a damper and the crankshaft, the twisting and resulting resonance of the crankshaft can be lowered or counteracted at higher speeds. Weights added to the crankshaft are one example of a friction damper.

SUMMARY OF THE INVENTION

A pump in which torsional energy from a shaft is converted to high pressure, actuating the pump. The pump is comprised of a ring, a housing, a rotor, first and second return springs, inlet passages, and outlet passages. The ring surrounds and is fixedly attached to a housing. The rotor connects to a shaft coaxially located within the housing. The housing and the rotor define at least one vane separating a chamber in the housing into an advance and a retard chamber. A first return spring is received between the housing and the vane in the advance chamber and a second return spring is received between the housing and the vane in the retard chamber. Inlet passages are present between a supply and the advance chamber and the supply and the retard chamber. Each of the passages have at least one inlet check valve. Outlet passages are present between the advance chamber and an output and the retard chamber and an output. Each of the passages has at least one outlet check valve.

The shaft may be rotating or non-rotating. The rotating shaft may be a crankshaft or a camshaft. The non-rotating shaft may be variable displacement control shafts or other shafts that have reciprocating motion.

In another embodiment, the torsional pump uses the torsional energy from the shaft to damper or eliminate torsional vibration of a crankshaft over the entire speed range of the engine, instead of just at the crankshaft resonance speed.

BRIEF DESCRIPTION OF THE DRAWING Fig. 1 shows a graph of the filing frequency order and the fourth order of resonance as related to crank oscillation and average speed.

Fig. 2 shows a graph of the tuned absorber signal and the crank resonance as related to crank oscillation and average speed.

Fig. 3 shows a graph of the torsional pump resonance of the present invention and the crank resonance as related to crank oscillation and average speed.

Fig. 4 shows a graph comparing the output pressure of the torsional pump of the present invention and the output pressure of a conventional pump as related to pressure, speed, and the amount of pressure need by the engine.

Fig. 5 shows a graph comparing the output pressure of the torsional pump of the present invention and the output pressure of a downsized conventional pump as related to pressure, speed, and the amount of pressure needed by the engine.

Fig. 6 shows a schematic of the torsional pump of the present invention showing a pumping loop with negative torque pulses.

Fig. 7 shows a schematic of the torsional pump of the present invention showing a pumping loop with positive torque pulses.

Fig. 8 shows an exploded view of the torsional pump of the present invention.

Fig. 9 shows a top view of the torsional pump of the present invention.

Fig. 10 shows an isometric view of the torsional pump of the present invention.

Fig. 11 shows a side view of the torsional pump of the present invention.

Fig. 12 shows a schematic of a torsional pump of an alternate embodiment showing a pumping loop with negative torque pulses.

Fig. 13 shows a schematic of a torsional pump of an alternate embodiment showing a pumping loop with positive torque pulses. DETAILED DESCRIPTION OF THE INVENTION

Figures 6 through 11 show a torsional pump of a first embodiment that uses torsional energy from a rotating shaft or a non-rotating shaft to function. An inertia ring Ib and a mating housing Ia, form a complete housing 1 that surrounds a rotor 3 attached to a rotating shaft or a non-rotating shaft 22. The inertia ring Ib has the necessary mass to delay or lag the motion of the ring so that there is relative motion between the rotor 3 and the housing Ia. The rotor 3 has one or more vanes 6 mounted to the end of the shaft 22, which are surrounded by the housing 1. The housing 1 and the rotor 3 form chambers into which the vanes fit. The vanes 6 separate each chamber into an advance chamber 2 and a retard chamber 4. An advance return spring 18 is present in the advance chamber 2 with one end of the spring 18 received by a bore 25 a in the mating housing Ia and the other end received by a bore 6a in the vane 6. A retard return spring 17 is present in the retard chamber 4 with one end of the spring 17 received by a bore 25b in the mating housing Ia and the other end received by a bore 6b in the vane 6. The return springs 17, 18 keep the rotor 3 in between the ends stops, preventing the vane 6 from slamming into the mating housing Ia on either side of the vane 6 and allowing the position of the rotor 3 to be adjusted.

Referring to Figure 8, a front end plate 23 is placed relative to one side of the housing 1 and an end plate 21 is placed on the other side of the housing 1 and receives the shaft 22. The front end plate 23 is secured to the rotor 3 and the end plate 21 using bolts

24.

The pump supply 8 supplies fluid through line 16 to either the advance chamber 2 through inlet check valve 14 and inlet line 19 or to the retard chamber 4 through inlet check valve 15 and inlet line 20. Fluid exits the advance chamber 2 through outlet line 12, outlet check valve 5, and outlet line 10 to the output flow line 9. Fluid exits the retard chamber 4 through outlet line 13, outlet check valve 7, and outlet line 11 to the output flow line 9. The output flow from line 9 and the pressure may be used for general engine lubrication and other hydraulic devices in the engine such as hydraulic tensioners, hydraulic lash adjusters, and piston squirters. The housing 1 has a large inertia so that when the input shaft 22 has some torsional excitation the motion of the housing 1 will lag the rotor 3 so that there is some relative motion between the rotor 3 and the housing 1. When the shaft's torsional energy is positive, as shown in Figure 6, oil or hydraulic fluid is pushed out of the retard chamber 4 into line 13 and through outlet check valve 7 to line 11 and the output flow line 9. At the same time, pump supply 8 supplies fluid through line 16 and inlet check valve 14 to line 19 and the advance chamber 2.

When the shaft's torsional energy switches from positive to negative, hydraulic fluid is pushed out of the advance chamber 2 into line 12 and through outlet check valve 5 to line 10 and the output flow line 9. At the same time, pump supply 8 supplies fluid through line 16 and inlet check valve 15 to line 20 and the retard chamber 4 as shown in Figure 7. In this embodiment, the oil pressure from the pump supply 8 varies, depending on the torsional input.

Figures 12 and 13 show a torsional pump of another embodiment that uses torsional energy from a rotating or non-rotating shaft to function. An inertia ring Ib and a mating housing Ia, forming a complete housing 1 that surrounds a rotor 3 attached to a rotating shaft or a non-rotating shaft 22. The inertia ring Ib has the necessary mass to delay or lag the motion of the ring so that there is relative motion between the rotor 3 and the housing Ia. The rotor 3 has one or more vanes 6 mounted to the end of the shaft 22, which are surrounded by the housing 1. The housing 1 and the rotor 3 form chambers into which the vanes fit. The vanes 6 separate each chamber into an advance chamber 2 and a retard chamber 4. An advance return spring 18 is present in the advance chamber 2 with one end of the spring 18 received by a bore 25a in the mating housing Ia and the other end received by a bore 6a in the vane 6. A retard return spring 17 is present in the retard chamber 4 with one end of the spring 17 received by a bore 25b in the mating housing Ia and the other end received by a bore 6b in the vane 6. The return springs 17, 18 keep the rotor 3 in between the ends stops, preventing the vane 6 from slamming into the mating housing Ia on either side of the vane 6 and allowing the position of the rotor 3 to be adjusted. The pump supply 8 supplies fluid through line 16 to either the advance chamber 2 through inlet check valve 14 and inlet line 19 or to the retard chamber 4 through inlet check valve 15 and inlet line 20. Fluid exits the advance chamber 2 through outlet line 12, outlet check valve 5, outlet line 10, and the output flow line 9 to the accumulator (not shown) and the regulator valve 30. Fluid exits the retard chamber 4 through outlet line 13, outlet check valve 7, outlet line 10, and the output flow line 9 to the accumulator (not shown) and the regulator valve 30. The regulator valve 30 sets the pressure to a fixed value, but may adjust the pressure of the torsional pump depending on the operation conditions of the engine. The pressure regulator valve 30 is comprised of an exhaust passage 30b, a spool 31 with lands 31a, 31b received within a sleeve 30e for blocking passage to and from the exhaust line 30b, a spring 30a, and a piece 30c. The pressure from outlet flow line 9 biases one end of the spool 31 against the spring 30a, depending on how high the output pressure is. Once the fluid is regulated, it flows out of the valve 30 through the regulated pressure exhaust 30b. Fluid that is not regulated or whose output pressure is not high enough to bias the spool 31 against the spring 30a flows out of the valve 30 through exhaust 30d.

The housing 1 has a large inertia so that when the input shaft 22 has some torsional excitation the motion of the housing 1 will lag the rotor 3 so that there is some relative motion between the rotor 3 and the housing 1. When the shaft's torsional energy is positive, as shown in Figure 12, oil or hydraulic fluid is pushed out of the retard chamber 4 into line 13 and through outlet check valve 7 to line 10 and line 9 and an accumulator (not shown) prior to entering the regulator valve 30. At the same time, pump supply 8 supplies fluid through line 16 and inlet check valve 14 to line 19 and the advance chamber 2.

When the shaft's torsional energy switches from positive to negative, hydraulic fluid is pushed out of the advance chamber 2 into line 12 and through outlet check valve 5 to line 10 and 9, and to the accumulator (not shown) and the regulator valve 30. At the same time, pump supply 8 supplies fluid through line 16 and inlet check valve 15 to line 20 and the retard chamber 4 as shown in Figure 13. The rotating shaft with torsional energy in the above embodiments may be camshafts and crankshafts. The non-rotating shaft of the above embodiments may be variable displacement control shafts and any shaft that has reciprocating motion.

The inertia ring Ib of the torsional pumps in the above embodiments may be used to drive the front end accessory drive (FEAD) belt or the vehicle's transmission.

The torsional pump of the above embodiments may also be used or applied to an engine or transmission of an automobile.

The torsional pumps of the above embodiments may be used as a friction type damper to prevent or help decrease crankshaft resonance. By taking some of the energy from the rotating or non-rotating shaft 22, and converting it to high pressure, the shaft torsional excitation can be reduced as shown in Figure 3. The pump can take the energy from the shaft 22 by adjusting the output pressure or flow out of line 9 or adjusting the flow rate of fluid into the pump from the pump supply 8. By using the torsional pump as a damper, the torsional vibration damper on a conventional rotating or non-rotating shaft may be eliminated and torsional vibration can be controlled over the entire speed range rather then just at the crankshaft resonance speed.

One example of using the torsional pump to reduce the oscillation of a shaft is to use the pump as an auxiliary pump for the engine lubrication system. The firing second order torsional energy of a crankshaft is very high at low speeds and the torsional pump would provide high pressure and flow at low speeds when the conventional engine pump output is low. Figure 4 shows a graph of the output pressure of a conventional pump and the torsional pump of the present invention as speed increases in comparison to the output pressure needed by the engine. The dashed line shows the output pressure needed from the pump as the engine speed increases. The unbroken line shows the output pressure of a conventional pump. The output pressure of a conventional pump is low when the speed of the engine is low, and does not meet the necessary pressure needed by the engine. As speed increases, the output pressure of the conventional pump increases. However, at high speeds, the output of the conventional pump is significantly greater than pressure actually needed by the engine. The output pressure of the torsional pump of the present invention is shown by the dash dot line and is high at low speeds and below what the engine requires at high speeds.

As the engine speed increases, the torsional pump output is reduced and the output of the conventional pump is increased. This helps balance the total oil output between the two pumps. Since conventional oil pumps are sized for hit idle conditions, it can be downsized, helping reduce the parasitic loses of the engine and improve the fuel economy. Figure 5 shows another graph of the output of pressure of the torsional pump of the present invention and a downsized conventional pump as speed increases in the comparison to the output of pressure needed by the engine. The dashed line shows the output pressure needed from the pump as the engine speed increases. The unbroken line shows the output pressure of a downsized conventional pump. The output pressure is mostly below the pressure required by the engine and reaches only slightly greater than the pressure required by the engine as speed increases. The output pressure of the torsional pump of the present invention is shown by the dash dot line and is high at low speeds and below what the engine requires at high speeds.

Accordingly, it is to be understood that the embodiments of the invention herein described are merely illustrative of the application of the principles of the invention. Reference herein to details of the illustrated embodiments is not intended to limit the scope of the claims, which themselves recite those features regarded as essential to the invention.

Claims

What is claimed is:

L A pump comprising:

a ring surrounding and fixedly attached to a housing;

a rotor for connection to a shaft coaxially located within the housing, the housing and the rotor defining at least one vane separating a chamber in the housing into an advance chamber and a retard chamber; the vane being capable of rotation to shift the relative angular position of the housing and the rotor;

a first return spring received between the housing and the vane in the advance chamber and a second return spring received between the housing and the vane in the retard chamber;

inlet passages between a supply and the advance chamber and the supply and the retard chamber, each passages having at least one inlet check valve; and

outlet passages between the advance chamber and an output and the retard chamber and an output, each passage having at least one outlet check valve;

wherein torsional energy from the shaft is converted to high pressure, actuating the pump.

2. The pump of claim 1, wherein the shaft is non-rotating.

3. The pump of claim 2, wherein the non-rotating shaft is a variable displacement control shaft or a shaft that has reciprocating motion.

4. The pump of claim 1, wherein the shaft rotates.

5. The pump of claim 4, wherein the rotating shaft is a camshaft or a crankshaft.

6. The pump of claim 1, wherein the ling drives the front end accessoiy drive.

7. The pump of claim 1, wherein the output is received by an accumulator and a pressure regulated valve.

8. The pump of claim 7, wherein the pressure regulator comprises: a spool slidably received within a sleeve, and a spring biasing the spool in a first direction, such that regulated pressure moves the spool in a second direction, opposite of the first direction and exhausts from a regulated pressure exhaust vent.

9. A pump comprising:

a iing surrounding and fixedly attached to a housing;

wherein torsional energy from the shaft is converted to high pressure, such that the torsional energy of the shaft is reduced.

10. The pump of claim 9, wherein the shaft rotates.

11. The pump of claim 10, wherein the shaft is a crankshaft or a camshaft.

12. The pump of claim 9, wherein the output flow from the output flow line is received by an accumulator and a pressure regulated valve.

13. A pump comprising:

a ring surrounding and fixedly attached to a housing;

wherein torsional energy from the shaft is converted to high pressure, such that the torsional vibration of the shaft is reduced and controlled over an entire speed range.