US3765445A - Dual crossover relief and case surge valve for hydraulic motors and pumps - Google Patents

Abstract

A valve is provided which will automatically respond to relieve overload hydraulic pressures in a hydraulic operating device such as a motor or pump, being mounted directly in the housing of the device and operatively communicating with the hydraulic operating circuit to bypass hydraulic pressure automatically when an overload in the device is sensed by the valve.

Description

' United States Patent [191 Schultz 1 Oct. 16, 1973 [54] DUALCROSSOVER RELIEF AND CASE 2,954,052 9/1960 Krehbiel 137/612.1 SURGE VALVE FOR HYDRAULIC MOTORS 2,989,072 6/1961 Banker 137/493 UX AND PUMPS 3,252,698 5/1966 Perrone 137/493 2,904,066 9/1959 Freeman 137/493 [76]- lnventor: John Clayson Schultz, 40 Homesgarth Ave Buffalo FOREIGN PATENTS OR APPLICATIONS Fi]ed pt' 3 1 901,061. 7/1962 Great Britain 137/493 pp 185,206 Primary Examiner-Henry T. Klinksiek Related US. Application Data Attorney-Carlton Hill et [62] Division of Ser. No. 15,778, March 2, 1970, Pat. No.

- 3,663.124. v g 57] ABSTRACT v 52 us. ca. 137/493 valve is Provided which. will aummatimny respmd 51 im. c1. Fl6k 17/26 to relieve Overload hydraulic Pressures in a hydraulic. [58] Field of Search. 137/493, 4 93.8, 596, P device as a Pump being 13759612 59613, 6121. 91/437,494 mounted directly in the housing of the device and opr eratively communicating with the hydraulic operating [56] References Cited; circuit to bypass hydraulic pressure automatically UN'ITEI'j STATES PATENTS when an overload in the device is sensed by the valve.

2,665,708 1/1954 Ghormley 137/493 6 Claims, 4 Drawing Figures PATENTEU UN 16 I975 SHEET 1 OF 2 llllllllllll/ DUAL CROSSOVER RELIEF AND CASE SURGE .VALVE FOR HYDRAULIC MOTORS AND PUMPS The presentapplication is a division of my copending application Ser. No. 15,778 filed Mar. 2, 1970, now U.S. Pat. No. 3,663,124 dated May 16, 1972.

This invention relates to safety valve structure, and is more particularly concerned with such a valve which is especially useful in association with hydraulic motors or pumps.

In the operation of hydraulic devices such as motors or pumps, conditions of control sometimes occur wherein the hydraulic operating fluid passages to and from the device are abruptly closed. Due to the inertia of the rotating parts of the device and whatever it is driving or by whatever it is driven, rotation tends to continue. Excessive pressures may therefore develop which can result in structural damage to the device and the hydraulic lines. Heretofore in such hydraulic devices intended to operate in both directions of rotation, it has been deemed necessary to provide two relief valves, or a complex arrangement including a system of check valves. Furthermore, there has been some problem with having the relief valve structure located close enough to the hydraulic ports in the system of the device to attain rapid enough response to minimize peak surges.

Where the hydraulic device has a case chamber to I which hydraulic fluid leaks, intentionally or otherwise, during operation, a situation may occur wherein the pressure may rise in the case chamber to an excessive and possibly damaging level. Heretofore separate pressure relief means have generally been considered necessary to take care of such case pressure overload.

According to the present invention, the foregoing and other disadvantages, shortcomings, inefficiencies and problems are overcome by providing a new and improved valve means which will, in a single functional assembly, meet all requirements.

An important object of the invention is to provide in one valve assembly means for relieving overload pressures in either direction of rotation of a hydraulic device such as a motor or pump.

Another object of the invention is to provide a new and improved overload relief valve structure which can be simply and efficiently installed directly in association with port cavities in a hydraulic device soas to become a functionally integral part of the device.

Still another object of the invention is to provide a new and improved pressure relief valve for hydraulic devices such as motors and pumps and which will eliminate the need for the usual check valve system.

A yet further object of the invention is to provide a new and improved simplified, highly efficient and reliable pressure relief valve structure for hydraulically operating devices.

Other objects, features and advantages of the invention will be readily apparent from the following description of a preferred embodiment thereof, taken in conjunction with the accompanying drawings, although variations and modifications may be effected without departing from the spirit and scope of the novel concepts embodied in the disclosure, and in which:

FlG. is a vertical longitudinal sectional elevational view through a representative motor embodying features of the invention;

FIG. 2 is a fragmentary vertical longitudinal sectional detail view on an enlarged scale showing the control valve in one of its pressure relief functions;

FIG. 3 is a similar view showing the control valve in another of its pressure relieving functions; and

FIG. 4 is a similar view showing the control valve in a third of its pressure relieving functions.

By way of practical example, a pressure relief valve 5 is illustrated which is especially adapted for relieving excessive hydraulic pressures under a plurality of operating conditions in a hydraulic device 7 such as a motor or pump exemplified in FIG. -1 as of the low sp'eedhigh torque reciprocating piston type. Reference may be had to Kimsey U.S. Pat. No. 3,036,557 for a more detailed disclosure of this type of motor or pump. For thepresent purposes it is believed adequate to point out that in such a hydraulic device a rotary shaft 8 is mounted on roller bearings 9 in ahousing 10. One end portion 11 of the shaft extends from one end of the housing to be keyed to a driven or driving member where the housing is stationarily mounted as by attachment of ears or lugs 12 thereon to a support. On the other hand, the shaft 11 may be held stationary and the housing rotatably driven, as preferred.

Rotary relative movement between the shaft 8 and the housing 10 is effected by hydraulic pressure within the housing acting on the shaft where the device is to operate as a motor, or hydraulic pressure may be created by the device where it is to act as a pump. For this purpose, the shaft 8 has an eccentric 13 intermediate its ends within the housing 10 engaged thereabout by a bearing block 14 which has a plurality such as five outer perimeter substantially flat faces 15 toward the ends of-which respective pistons 17 reciprocable in cylinders 18 thrust operatively. Hydraulic pressure fluid such asoil is conveyed to and from the pistons 17 by means of a hydraulic system including a pair of parallel spaced longitudinal ducts l9 and 20 having respective ports 21 and 22 opening through the eccentric 13 to communicate cyclically with the pistons. These ducts extend from an inner end portion of the shaft 8, that is opposite to the outward extension 11, and communicate by way of axially spaced ports 23 and 24 respectively with annular transmission grooves 25 and 27, respectively, in the housing which'are suitably connected with hydraulic conduits in the associated hydraulic system. Normal leakage into a case chamber 28 is bled off by say of a scavenging duct 29.

Construction and arrangement of the relief valve 5 is such that it will respond to and relieve excessive pressure build up reflected in either of the transmission passages or grooves 25 and 27 or the case chamber 28. To this end, the valve assembly is mounted in a bore 30 provided in what may be referred to as the rear end portion ofthe housing 10 on an axis parallel to the shaft 8 but spaced therefrom and opening rearwardly from the housing. Within the bore 30 is received a generally cup-shaped valve retainer 31 retained against outward displacement by means comprising a snap ring 32.

7 Within a blind end inwardly opening bore 33 of the repast the valve member in the bore 33 is prevented by a dynamic ring seal 39.

Normally, under the bias of the spring 35, the valve member 34 closes a crossover port between the transmission groove passages 25 and 27 and defined by an annular valve seat 40 which is provided on a stepped juncture with an inwardly extending reduced diameter portion 41 of the bore 30 into which the valve member extends and which is desirably of the same diameter as the bore 33 of the retainer 31 so that both opposite end portions of the valve member 34 are of the same diameter. In normal sealing engagement with the seat 40 is a poppet shoulder 42 located intermediately on the spool valve member 34 and comprising a frust'o-conical area extending from an annular flange 43, of'larger diameter than the remainder of the valve member, into an annu-' lar groove 44 of substantial length providing a reduced diameter on the member between the shoulder 42 and an inner end head portion 45 of the valve member carrying a peripheral dynamic ring seal 47 engaging the bore portion 41. Communication between the bore portion 41 and the groove 44 and the transmission passage groove 25 of the housing is effected through apassage extension 48. At the outer side of the crossover port valve seat 40 communication is effected between the transmission passage 27 and the larger diameter portion of the bore 30 between'the seat 40 and the inner end of the retainer 31 by way of a branch passage 49. 1

While the pressure in the operating circuit of the device 7 is within a safe range as reflected in either of the passages 25 and 27 and as referenced to the valve'assembly by way of the normally non-communicating branch passages 48 and 49, respectively, the biasing spring 35 retains the valve member 34 in the crossover port blocking, sealing position as shown in FIG. 1. Should excessive pressure develop in either of the passages 25 or 27, the valve member 34 will respond in opposition to the bias of the spring 35 and open the crossover port to bypass the excessive pressure to the low pressure side of the circuit represented by the other of the passages. To effect this with a minimum size biasing spring, the valve member 34 is provided with hydraulic fluid thrust surfaces which are nearly in-balance on both sides of the crossover port seat 40, but sufficiently out of balance in the outward direction of the valve to be responsive to the overload or excessive hydraulic pressure at either side of the crossover port to shift the valve member and effect hydraulic pressure relief.

Assuming that the hydraulic device 7 is operating in a fashion wherein the transmission passage 27 is on the high pressure side of the system and the transmission passage 25 is on the low pressure side, the pressure on the opposit sides of the annular flange 43 is substantially balanced. Should there be an overload pressure referenced to the valve from the passage 27, this will be felt internally within the valve member 34, as indicated in FIG. 2 through a port 50 extending radially inwardly adjacent to the outer side of the flange 43 and whereby the overload pressure is referenced to a thrust surface 51 at the blind end of a bore extending through the valve member from the blind end and opening through the inner end of the valve member. To contain the pressure on the thrust surface 51, means comprising a plunger 53 are provided closing the bore 52 inwardly from the reference port 50 and slidably in the bore 52 so that the pressure thrusts the plunger inwardly toward an inner blind end shoulder 54 of the bore portion 41. Since the valve member 34 and the plunger 53 are relativelyifreciprocable, the combined pressure area provided by the shoulder 42 and the thrust surface 51 overbalances pressure on the outer side of the flange 43 and overcomes the bias of the spring 35 to shift the valve member 34 outwardly, thus opening the crossover port defined by the valve seat 40 thereby dumping the overload pressure thorugh the crossover port into the passage 25 by way of the passage extension 48.

Similarly, where the transmission passage 25 is in the high pressure side of the hydraulic system and the passage 27 is in the low pressure or exhaust side of the system, should a pressure overload develop in the passage 25, such overload is referenced by way of the passage extension 48 and through a radial reference port 55 (FIG. 3) in the small diameter portion 44 of the valve member to thrust surface bore 52,as indicated by directional arrows. Thereby, the overload pressure thrust outwardly relative to the valve member 34 onto the adjacent end of the plunger 53 which thereby thrust against the thrust surface 51 to add the area of-such thrust surface to the area of the shoulder 42 exposed to the overload pressure, overbalancing the pressure against the shoulder of the valve head 45 and overcoming bias of the spring 35-to move the valve shoulder from the seat 40 thereby to open the crossover port and thus dump the overload pressure into the low pressure side of the system by way of the branch passage 49 and the transmission passage 27. During such .an occurence, a plunger 57 reciprocable in the bore 52 inwardly relative to the reference port 55 contains the pressure between the inner end of the plunger 57 and the plunger 53 while remaining stationary relative to the valve member 34 by thrusting against the dead-end shoulder 54 as a stop. In order to maintain the adjacent ends of th plungers 53 and 57 normally separated and at all times clear of the reference port 55, one of the plungers, herein'the plunger 53, is provided with a reduced diameter spacing extension 58. Similarly to maintain the opposite end of the plunger 53 clear of the reference port 50, a reduced diameter spacing extension 59 is provided thereon which in the outward pressure relief thrusting of the plunger 53 makes the actual engagement with the thrust surface 51.

In yet another pressure relieving response, the valve member 34 is adapted to be shifted outwardly against the bias of the spring 35 to move the valve shoulder 42 from the seat40 to open the bypass port when an overload hydraulic pressure develops in the case chamber 28, as depicted in FIG. 4. When this occurs, the case overload pressure is referenced through a port or passage ,60 through the stop surface 54 onto the inner end of the valve member 34, and more particularly the inner end of the head 45 whereby to thrust the valve member in an outward direction, the entire area of the valve head end, including the area of the bore 52 being responsive to the pressure by virtue of the plunger 57 blocking the inner end portion of the bore as shown. Opening of the crossover port by action of the case pressure overload causes bypassing of pressure from whichever of the passages 25 or 27 is on the high pressure side to the other of the passages which is on the low pressure side at the particular occurrence, thus relieving the hydraulic device of internal pressure until the case pressure has resumed a safe pressure level.

From the foregoing, it will be appreciated that in one relatively simple, possitively acting valve unit 5, anyone of the plurality of hyhdraulic overload hazards that may occur in the hydraulic device 7 are avoided efficiently by direct, short range communication with the areas in which the overload pressures may develop.

It will be understood that variations and modifications may be effected without departing from the scope of the novel concepts of the present invention.

I claim:

1. In a valve assembly including a housing having therein a valve bore and a pair of passages communicating with said bore intermediate its ends and in spaced relation to one another, there being a valve seat in said bore between said passages:

a spool valve member having respective opposite end portions slidably engaged with surfaces within said bore beyond the communicating passages in each longitudinal direction of the valve member;

a frusto-conical poppet shoulder located intermediately on the valve member and providing pressure responsive area extending in part to one side of said valve seat and part to the other side of said valve seat in the seated engagement of said poppet shoulder with the valve seat;

biasing means normally thrusting against one end of the valve member to effect engagement by said poppet shoulder sealingly against said valve seat to close off communication between said passages through a passageway through said valve seat;

a blind end bore longitudinally in said valve member opening through the opposite end of said member and having a port opening radially thereinto from the perimeter of the valve member at one side of said poppet shoulder and another port opening radially thereinto from the perimeter of the valve member at the opposite side of said poppet shoulder;

a first plunger slidably located in said member bore between said ports;

a second plunger slidably mounted in said member bore and projectable from said opposite end of the member; and

means for maintaining said first plunger spaced from the blind end of the member bore and spaced from said second plunger in any operating relationship of the plungers within the member bore;

whereby high pressure differential in either of said passages acts on said poppet shoulder and through the port nearest to such high pressure differential passage and within said member bore and either between said first plunger and the blind end of the member bore or between said plungers, as the case may be, to effect displacement of said valve member in opposition to the biasing means for passage of high pressure fluid through said passageway to the other of the passages.

2. A valve assembly according to claim 1, wherein said means for spacing said first plunger comprise reduce diameter spacing extensions at the opposite ends thereof.

3. A valve assembly according to claim 1, wherein said biasing means comprise a coiled compression spring, and a cup-shaped valve retainer mounted in an enlarged diameter portion of said housing bore and supporting said spring and slidably engaged by the one portion of said valve member.

4. A valve assembly according to claim 3, said valve member having a radial flange opposing an inner end on said retainer and being normally in spaced relation thereto under the bias of said spring.

5. A valve assembly according to claim 3, said valve seat being located at juncture of said larger diameter portion of said housing bore and the remaining portion of said housing bore.

6. A valve assembly according to claim 1, including a passage communicating with a blind end of said housing bore for impressing pressure fluid on the adjacent end of said valve member and said second plunger for shifting the valve to unseat said shoulder from said valve seat.

UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No. 3, 765, 445 4 Dated October 16, 1973 Inventor(s) John Clayson Schultz It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shown below:

Column 2, line 48, for "say" read --way-,

Column line 9, for "thorughff read -through--;

- line 38, for "th" read --the--.

Signed and sealed this 16th day of April 197M.

(SEAL) Attest:

EDWARD .PLFLETCHEILJR. 0. MARSHALL DANN Attest'ing Officer Commissioner of Patents

Claims (6)

1. In a valve assembly including a housing having therein a valve bore and a pair of passages communicating with said bore intermediate its ends and in spaced relation to one another, there being a valve seat in said bore between said passages: a spool valve member having respective opposite end portions slidably engaged with surfaces within said bore beyond the communicating passages in each longitudinal direction of the valve member; a frusto-conical poppet shoulder located intermediately on the valve member and providing pressure responsive area extending in part to one side of said valve seat and part to the other side of said valve seat in The seated engagement of said poppet shoulder with the valve seat; biasing means normally thrusting against one end of the valve member to effect engagement by said poppet shoulder sealingly against said valve seat to close off communication between said passages through a passageway through said valve seat; a blind end bore longitudinally in said valve member opening through the opposite end of said member and having a port opening radially thereinto from the perimeter of the valve member at one side of said poppet shoulder and another port opening radially thereinto from the perimeter of the valve member at the opposite side of said poppet shoulder; a first plunger slidably located in said member bore between said ports; a second plunger slidably mounted in said member bore and projectable from said opposite end of the member; and means for maintaining said first plunger spaced from the blind end of the member bore and spaced from said second plunger in any operating relationship of the plungers within the member bore; whereby high pressure differential in either of said passages acts on said poppet shoulder and through the port nearest to such high pressure differential passage and within said member bore and either between said first plunger and the blind end of the member bore or between said plungers, as the case may be, to effect displacement of said valve member in opposition to the biasing means for passage of high pressure fluid through said passageway to the other of the passages.

2. A valve assembly according to claim 1, wherein said means for spacing said first plunger comprise reduce diameter spacing extensions at the opposite ends thereof.

3. A valve assembly according to claim 1, wherein said biasing means comprise a coiled compression spring, and a cup-shaped valve retainer mounted in an enlarged diameter portion of said housing bore and supporting said spring and slidably engaged by the one portion of said valve member.

4. A valve assembly according to claim 3, said valve member having a radial flange opposing an inner end on said retainer and being normally in spaced relation thereto under the bias of said spring.

5. A valve assembly according to claim 3, said valve seat being located at juncture of said larger diameter portion of said housing bore and the remaining portion of said housing bore.

6. A valve assembly according to claim 1, including a passage communicating with a blind end of said housing bore for impressing pressure fluid on the adjacent end of said valve member and said second plunger for shifting the valve to unseat said shoulder from said valve seat.

Images