201107604 六、發明說明： 【發明所屬之技術領域】 本發明是有關於一種齒輪式油泵，特別是指一種外接 齒輪式油泵。 【先前技術】 齒輪式油泵，是液壓泵種類中結構最簡單且最常被使 用的’依據結構可粗略區分成外接齒輪式與内接齒輪式兩 種’其中以外接齒輪式油泵的應用最為廣泛m在車 輛潤滑系統中而用來輸送機油的齒輪式㈣為例，主要是 ^ 3個果威、一個與該泵殼鎖固在一起的栗蓋，以及二 個相嗤合旋轉地容置在該系殼與該聚蓋間的齒輪。該二個 齒輪將該栗殼與該果蓋間的密閉空間區分成一吸油腔與一 排油腔。 *引擎的曲轴7P*動該二齒輪相哨合轉動時，能將油底 殼中的機油吸入該吸油腔中，機油進而流進入該二齒輪的 位在該吸油腔處的各齿縫内以被夹帶往該排油腔處，待該 Γ齒輪相唾合時，便得以將位在齒縫中的機油加壓擠出至 排油腔中’所w，隨著該二齒輪在固定轉速下持續地轉 私鳴合，該排油腔便能不斷地排出固定流量的機油，並 、旧至-主油道中，使得如凸輪軸、曲轴、連桿、活塞 主轴承、汽紅壁..·等機件能獲得油潤而順暢運轉。 -釋H通$會在㈣輪式衫的出口與主油道間裝設 釋壓閥，以當該齒輪式油泵的 間能將該齒輪所輪時^亥釋愿 翰出的多餘機油，導回油底 201107604 殼或該齒輪式油泵中。 然而n玄齒輪式油果的出口所排出的果流量是持 續且固定的，造成該釋壓閥於洩壓速率上較為緩慢，如此 -來，在長時間的高排油阻力環境下，引擎的曲軸為了維 持該齒輪式油泵的齒輪_定轉速，相對得耗費更大的驅 動電能’而且，該釋壓閥必須長時間維持在開啟狀態，以 致壽命較短。 【發明内容】 因此，本發明之目的，即在提供一種透過改變泵流量 方式’以能迅速控制油壓，且兼具節能省電效能的齒輪式 油泵。 於是，本發明之齒輪式油泵，包含一泵殼、一與該泵 殼組合在一起並相配合界定出一輸油空間的泵蓋、二相嚙 合旋轉地容置在輸油空間中的齒輪，以及一洩壓閥。該二 齒輪將該輸油空間區分成一吸油腔’以及一排油腔。該洩 壓閥具有一連通該排油腔與該吸油腔之中空的座體以及 一能滑移地設置在該座體中的閥塞；該閥塞能受該排油腔 之油壓影響而相對該座體在一非洩油位置與一洩油位置間 往復滑移，在該非洩油位置時，該吸油腔不洩油，而在該 洩油位置時’該吸油腔則茂油。 本發明之功效在於，當該排油腔的油壓過大時，便會 迫推泫閥塞移動至該洩油位置，促使該吸油腔進行洩油， 如此能立即降低泵流量，達到迅速調解油壓與節省驅動電 能消耗等功效。 201107604 【實施方式】 有關本發明夕a 73 <則述及其他技術内容 '特點與功效，在 以下配合參考_ > 固式之一個較佳實施例的詳細說明中，將可 清楚的呈現。201107604 VI. Description of the Invention: [Technical Field] The present invention relates to a gear type oil pump, and more particularly to an external gear type oil pump. [Prior Art] The gear type oil pump is the simplest and most commonly used structure of the hydraulic pump type. The structure can be roughly divided into the external gear type and the internal gear type. The external gear type oil pump is the most widely used. For example, in the vehicle lubrication system, the gear type (4) used to convey the oil is mainly three cores, a chestnut cover that is locked with the pump casing, and two rotatively accommodated in the same a gear between the shell and the cover. The two gears divide the confined space between the chestnut shell and the fruit cover into an oil suction chamber and an oil discharge chamber. * The crankshaft 7P* of the engine can move the oil in the oil sump into the oil suction chamber when the two gears rotate in the whistle, and the oil flows into the teeth of the two gears at the joints of the oil suction chamber. Entrained to the oil discharge chamber, when the Γ gear is salvaged, the oil in the tooth gap can be squeezed out into the oil discharge chamber, as the two gears are at a fixed speed Under the continuous whistle, the oil draining chamber can continuously discharge the fixed flow of oil, and the old to the main oil passage, such as the camshaft, crankshaft, connecting rod, piston main bearing, steam red wall.. The machine can be operated smoothly and smoothly. - Release H-pass will install a pressure relief valve between the exit of the (four) wheel-type shirt and the main oil passage, so that when the gear-type oil pump can rotate the gear, it will release the excess oil from the machine. Return to the bottom of the 201107604 shell or the gear pump. However, the fruit flow discharged from the outlet of the n-gear-type oil fruit is continuous and fixed, causing the pressure-relief valve to be slow in the pressure-relieving rate, so that, in the long-term high oil-displacement resistance environment, the engine In order to maintain the gear speed of the gear pump, the crankshaft relatively consumes a larger amount of driving power. Moreover, the pressure relief valve must be maintained in an open state for a long time, so that the life is short. SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a gear type oil pump which can quickly control the oil pressure by changing the pump flow rate, and which has both energy saving and power saving performance. Therefore, the gear type oil pump of the present invention comprises a pump casing, a pump cover which is combined with the pump casing and cooperates to define an oil supply space, and a gear which is rotatively accommodated in the oil transportation space by two phases. And a pressure relief valve. The two gears divide the oil transfer space into an oil suction chamber and a row of oil chambers. The pressure relief valve has a hollow seat communicating with the oil discharge chamber and the oil suction chamber and a valve plug slidably disposed in the seat body; the valve plug can be affected by the oil pressure of the oil discharge chamber The housing is reciprocally slid between a non-discharging position and a drain position. In the non-discharging position, the oil suction chamber does not drain oil, and in the drain position, the oil suction chamber is oily. The effect of the invention is that when the oil pressure of the oil discharge chamber is too large, the valve plug is forced to move to the drain position, and the oil suction chamber is caused to drain oil, so that the pump flow can be immediately reduced, and the oil can be quickly adjusted. Pressure and save drive power consumption and other effects. [Embodiment] The present invention will be clearly described in the detailed description of a preferred embodiment of the present invention.
如圖1〜圖3路- I 厅不，本發明齒輪式油栗2的一較佳實施 例’疋设置在-車輛的潤滑系統（圖中未示）中，能被引 擎的曲軸（或凸輪轴）帶動，以將一油底殼中的機油吸取並加 壓送5 —主、’i、若 _ 中，使得如凸輪軸、曲軸、連桿、活塞、 主軸承、汽缸壁...等機件能獲得油潤而順暢運轉。 該齒輪式H 2包含—泵殼21、-與料殼21鎖固在 起的泵蓋22、二相嚙合旋轉地容置在該泵殼21與該泵蓋 . 22之間的齒輪23、24 ,以及一設置在該泵蓋22之一表面 上的洩壓閥25。 該泵殼21與該泵蓋22相配合界定出一輸油空間21〇， °亥輸油空間210具有—被該二齒輪23、24所區分出的吸油 鲁腔211、排油腔212，以及一岔接該吸油腔21丨且不連通該 排油腔212的洩油道213 ;該泵蓋22具有一連通該吸油腔 211之一起端的進油口 221，以及一連通該排油腔212之一 、、、《鸲的出油口 222。該齒輪23是受引擎之曲軸驅動而往順 時針方向旋轉，進而驅使相嚙合之該齒輪24往逆時針方向 轉動。 - 該洩麼閥25具有一橫置在該泵蓋22的表面上且其一 左、右端261 ' 262皆呈開放狀之中空柱狀的座體251、二 分別插設在該座體251之左、右端261、262處的栓塞252 201107604 、一可往復橫向滑移地嵌塞在該座體251中的閥塞253，以 及一設置在該座體251中且能施予該閥塞253 一左移推力 的彈性件254。 該座體251具有一靠近其左端261且與該排油腔212 相連通的旁通孔255、一靠近其右端262且連通該洩油道 213的一端的開關孔256，以及一與該開關孔256分別位在 其一徑線的相反二端處且能連通該開關孔256的洩油孔257 ，而在該閥塞253之阻隔下，該旁通孔255是無法與該洩 油孔257或該開關孔256相連通。該閥塞253是概呈橫倒 式沙漏狀，並具有一相對於位在左邊之栓塞252的第一均 徑端部258、一相反於該第一均徑端部258且相對於位在右 邊之栓塞252的第二均徑端部2M，以及一連結該第一、二 均徑端部258、259的縮徑部250，該第一、二均徑端部 258、259的直徑長度是等於該座體251的内徑長度。該彈 性件254的一左、右端271、272是分別連結該閥塞253的 第二均徑端部259與位在右邊的栓塞252 ;本實施例中，該 彈性件是一壓縮彈簧。 如圖3與圖4所示，該閥塞253能相對該座體251在 一洩油位置與一非洩油位置間往復滑移。在該非洩油位置 (見圖3)時’該閥塞253是相對靠近該旁通孔255，且該 縮徑部250是完全偏離該開關孔256與該洩油孔257之間 ，而該第二均徑端部259g是擋阻在該開關孔256與該洩油 孔257之間’使得該開關孔256與該洩油孔257無法相連 通’另外，該彈性件254未被壓縮；而在該洩油位置（見 201107604 圖4)時’該閥塞253是相對遠離該旁通孔255，且該縮徑 部250是移進入該開關孔256與該洩油孔257之間，此時 該開關孔256與該洩油孔257相連通，同時該彈性件254 呈壓縮狀態。 該齒輪式油泵2於運作時，主要是利用該二齒輪23、 24相嚙合旋轉時’所造成該吸油腔211 (為低壓區）與該排 油腔212 (為高壓區）之間的壓差效應，以能吸取並排出預 定壓力與流量的機油，藉而將引擎之曲軸所輪入的機械能 予以轉換成液壓能。過程中，油底殼中的機油經由該進油 口 221被吸入該吸油腔211中後，會進入該二齒輪23、24 位在該吸油腔211側的各齒縫231、241内，並被夾帶往該 排油腔212處，直到該二齒輪23、24相嚙合，位在齒縫 231、241中的機油便被加壓擠出至該排油腔212中所以 ，隨著該二齒輪23、24在固定轉速下持續地轉動' 嚙合， 便能不斷地經由該排油腔212、該出油口 222排出固定排量 與流量的機油。其中，排量的定義是曲軸帶動該二齒輪汨 、24旋轉一周時所排出的機油體積，單位為立方公分/轉（ cm3/rev·);而流量的定義是單位時間内所排出的機油體積， 早位為公升/分鐘（L/min )。 、 另一方面，由於排油壓力（就是排油腔212的壓力， 是與泵流量直接相關’以下稱油壓）、系流量是與該二齒輪 23、24的轉速成正比，也就是說，該二齒輪23、24的轉速 越大，栗流量與油壓皆越大，所以，透過該㈣閥25的設 計，能控制油壓維持在安全運作的限值範圍中，且所輪出 201107604 泵流量是符合需求而不過大，同時可避免驅動能量的過度 損耗。因此’復見圖3 ’當油壓處於正常的限值範圍且泵流 量適當時，從該排油腔212經由該旁通孔255而流進入該 座體251中的機油量不足，無法克服該彈性件的彈力 係數以推動該閥塞253，或是該閥塞253的右移量過少，使 得該閥塞253之縮徑部250是偏離該開關孔256與該洩油 孔257之間，該開關孔256與該洩油孔257因受該閥塞253 的第二均徑端部259阻隔而不相連通且各呈封閉狀態，該 洩油道213中的機油便無法排出。 相反地，復見圖4，當油壓已超出最大限值且泵流量過 大時，§亥排油腔212中的多餘機油量便會經由該旁通孔25 5 擠灌入該座體251中’而迫推該閥塞253的縮徑部250右 移至該開關孔256與該洩油孔257間，此時，該開關孔256 與該洩油孔257便能相通而各呈開啟狀態，讓該洩油道213 中的機油依序流經該開關孔256、該茂油孔257而外排出， 進而迴流至油底殼中；過程中，油壓越大且擠入該座體2 51 中的機油量越多，該閥塞253的右移距離與該彈性件254 的變形量便越大，相對會使該開關孔256與該洩油孔257 的開放程度增大，導致該吸油腔211的洩油量越多，直到該 縮徑部250完全移進入該開關孔256與該洩油孔257間， 使該開關孔256與該洩油孔257呈全開狀態，代表該閥塞 253已移動了最大右移距離，且該彈性件254是產生最大變 形量。 簡單來說，於該排油腔212過壓時，驅使該洩壓閥25 201107604 作動以洩放該吸油腔21丨中的機油，便能改變（縮小）該二 齒輪23、24的排量與泵流量，達到迅速排解該排油腔212 處的過大排油壓力與多餘泵流量的作用’同時因排油阻 力迅速減小，還能節省引擎的曲軸為維持該二齒輪23、Μ 的固定轉速所消耗的電能。而當油壓已降至正常的限值範 圍時，便不會再有多餘機油擠入該座體251令，該座體251 中的機油量減少，原本呈壓縮狀態的彈性件254得以釋出As shown in FIG. 1 to FIG. 3, a preferred embodiment of the gear type oil pump 2 is disposed in a lubrication system (not shown) of the vehicle and can be used by the crankshaft (or cam) of the engine. The shaft is driven to suck and pressurize the oil in an oil pan to 5 - main, 'i, if _, such as camshaft, crankshaft, connecting rod, piston, main bearing, cylinder wall, etc. The parts can be oily and run smoothly. The gear type H 2 includes a pump casing 21, a pump cover 22 that is locked with the casing 21, and two gears 23, 24 that are rotatably received between the pump casing 21 and the pump cover 22. And a pressure relief valve 25 disposed on a surface of one of the pump covers 22. The pump casing 21 cooperates with the pump cover 22 to define an oil transportation space 21〇, and the oil transportation space 210 has an oil absorption lumen 211 and an oil discharge chamber 212 which are distinguished by the two gears 23 and 24, and a drain passage 213 connected to the oil suction chamber 21 and not communicating with the oil discharge chamber 212; the pump cover 22 has an oil inlet 221 communicating with the same end of the oil suction chamber 211, and a communication port 212 communicating with the oil discharge chamber 212 I.,, "The oil outlet of the 222. The gear 23 is driven by the crankshaft of the engine to rotate clockwise, thereby driving the gear 24 that meshes in a counterclockwise direction. The venting valve 25 has a hollow cylindrical seat body 251 which is horizontally disposed on the surface of the pump cover 22 and has a left and right end 261 262 which are open, and is inserted into the seat body 251, respectively. a plug 252 201107604 at the left and right ends 261, 262, a valve plug 253 that is reciprocally laterally slidably embedded in the seat body 251, and a valve body 251 disposed in the seat body 251 and capable of applying the valve plug 253 The elastic member 254 of the thrust is moved to the left. The base 251 has a bypass hole 255 near the left end 261 and communicating with the oil discharge chamber 212, a switch hole 256 near the right end 262 thereof and communicating with one end of the drain passage 213, and a switch hole 256 are respectively located at opposite ends of one of the diameter lines and can communicate with the oil drain hole 257 of the switch hole 256. Under the barrier of the valve plug 253, the bypass hole 255 cannot be connected to the drain hole 257 or The switch holes 256 are in communication. The valve plug 253 is generally transversely hourglass-shaped and has a first mean diameter end 258 with respect to the plug 252 positioned to the left, a first opposite mean diameter end 258 and opposite to the right. a second mean diameter end portion 2M of the plug 252, and a reduced diameter portion 250 connecting the first and second mean diameter end portions 258, 259, wherein the first and second mean diameter end portions 258, 259 have a diameter length equal to The inner diameter of the seat body 251. A left and right ends 271, 272 of the elastic member 254 are respectively connected to the second mean diameter end portion 259 of the valve plug 253 and the plug 252 positioned on the right side; in the embodiment, the elastic member is a compression spring. As shown in Figures 3 and 4, the valve plug 253 is reciprocally slidable relative to the seat body 251 between a drain position and a non-discharge position. In the non-discharging position (see FIG. 3), the valve plug 253 is relatively close to the bypass hole 255, and the reduced diameter portion 250 is completely offset from the switch hole 256 and the drain hole 257, and the first The second mean diameter end portion 259g is blocked between the switch hole 256 and the drain hole 257 'so that the switch hole 256 and the drain hole 257 are not in communication'. In addition, the elastic member 254 is not compressed; The drain position (see 201107604 FIG. 4) is 'the valve plug 253 is relatively far from the bypass hole 255, and the reduced diameter portion 250 is moved between the switch hole 256 and the drain hole 257. The switch hole 256 communicates with the drain hole 257 while the elastic member 254 is in a compressed state. When the gear oil pump 2 is in operation, it mainly uses the pressure difference between the oil suction chamber 211 (which is a low pressure region) and the oil discharge chamber 212 (which is a high pressure region) when the two gears 23 and 24 are meshed and rotated. The effect is to absorb and discharge the oil of a predetermined pressure and flow rate, thereby converting the mechanical energy that the crankshaft of the engine enters into hydraulic energy. During the process, the oil in the oil pan is sucked into the oil suction chamber 211 through the oil inlet 221, and then enters the teeth 231, 241 of the two gears 23 and 24 on the side of the oil suction chamber 211, and is Entrained to the oil discharge chamber 212 until the two gears 23, 24 are engaged, the oil in the tooth gaps 231, 241 is pressurized and extruded into the oil discharge chamber 212, so that with the two gears 23 The 24 is continuously rotated at a fixed rotational speed to continuously discharge the fixed displacement and flow rate of oil through the oil discharge chamber 212 and the oil outlet 222. Wherein, the displacement is defined as the volume of oil discharged by the crankshaft to drive the two gears 汨, 24, and the unit is cubic centimeters per revolution (cm3/rev·); and the flow rate is defined as the volume of oil discharged per unit time. , the early position is liters / minute (L / min). On the other hand, due to the oil discharge pressure (that is, the pressure of the oil discharge chamber 212, which is directly related to the pump flow rate, hereinafter referred to as the oil pressure), the flow rate is proportional to the rotational speed of the two gears 23, 24, that is, The higher the rotational speed of the two gears 23 and 24, the greater the flow rate and the hydraulic pressure of the pump. Therefore, the design of the (four) valve 25 can control the oil pressure to be maintained within the safe operating limit range, and the pump is rotated 201107604. The flow rate is not too large to meet the demand, and excessive loss of driving energy can be avoided. Therefore, when the oil pressure is within the normal limit range and the pump flow rate is appropriate, the amount of oil flowing into the seat body 251 from the oil discharge chamber 212 via the bypass hole 255 is insufficient, and the The spring force coefficient of the elastic member pushes the valve plug 253 or the right shift amount of the valve plug 253 is too small, so that the reduced diameter portion 250 of the valve plug 253 is offset from the switch hole 256 and the drain hole 257. The switch hole 256 and the drain hole 257 are not connected to each other by the second mean diameter end portion 259 of the valve plug 253, and are each closed, and the oil in the drain passage 213 cannot be discharged. Conversely, as shown in Fig. 4, when the oil pressure has exceeded the maximum limit and the pump flow rate is too large, the excess oil in the sump oil chamber 212 is squeezed into the seat body 251 through the bypass hole 25 5 . 'When the diameter reducing portion 250 of the valve plug 253 is pushed to the right, the switch hole 256 is moved between the switch hole 256 and the drain hole 257. At this time, the switch hole 256 and the drain hole 257 can communicate with each other and are respectively opened. The oil in the oil drain 213 is sequentially discharged through the switch hole 256 and the oil hole 257 to be discharged outside, and then returned to the oil sump; in the process, the oil pressure is increased and the seat body 2 51 is extruded. The greater the amount of oil in the valve plug 253, the greater the distance of the right movement of the valve plug 253 and the amount of deformation of the elastic member 254, which relatively increases the degree of opening of the switch hole 256 and the drain hole 257, resulting in the oil suction chamber. The more the oil leakage amount of the 211 is, until the diameter reducing portion 250 completely moves between the switch hole 256 and the oil drain hole 257, so that the switch hole 256 and the oil drain hole 257 are fully opened, indicating that the valve plug 253 has been The maximum right shift distance is moved, and the elastic member 254 is the largest amount of deformation. Briefly, when the oil discharge chamber 212 is over-pressurized, the pressure relief valve 25 201107604 is actuated to discharge the oil in the oil suction chamber 21 , and the displacement of the two gears 23 and 24 can be changed (reduced). The pump flow rate can quickly resolve the excessive oil discharge pressure at the oil discharge chamber 212 and the excess pump flow rate. At the same time, the oil displacement resistance is rapidly reduced, and the crankshaft of the engine can be saved to maintain the fixed speed of the two gears 23 and Μ. The power consumed. When the oil pressure has dropped to the normal limit, no more oil will be squeezed into the seat 251. The amount of oil in the seat 251 is reduced, and the elastic member 254 which is originally compressed is released.
抗形變作用力來驅使該閥塞253自動左移復位，以停止該 吸油腔211繼續洩油。 如圖5所示，為該盘輪式油泵2於進行特性測試時所 呈現齒輪轉速與泵流量的關係，操作條件為：選用型號為 1谓40的機油，最大油溫值控制在125t，且最大油壓^控 制在bars。理論上，粟流量（或油壓）是與齒輪轉速: 線性關係（請見圖5的假想線所示），而齒輪轉速是引擎轉 速的二倍’所以’隨著齒輪轉速增大，栗流量（或油壓） 便可能過大而超出系統限值與實際需求；而由測試結果可 推知，當齒輪轉速在uoo〜2〇00轉/分鐘（rev/min)間時， _是符合系統限制與需求的’此時該㈣閥25並未作 動，也就是該吸油腔川油，所以此階段的泵流量與 齒輪轉速是略呈線性關係；而當齒輪轉速大於2_轉/分鐘 時’泵流量已過大’該祕閥25立刻作動以開始使該吸油2 腔2U中的機油經由該洩油道213洩出，所以，從圖中明顯 可見泵流量隨齒輪轉速上升的增加幅度已有趨緩，此時所 輸出果流量依然能符合系統需求。同理可證的，該齒輪式 201107604 油果2的齒輪轉速與油壓間也會呈現出類似的特性曲線關 係。 所以’利用該洩壓閥25的設計，當該排油腔212的油 壓與流置過大時，多餘的機油便推移該閥塞253以使該開 關孔256與該洩油孔257相通，讓該吸油腔211中的機油從 該洩油道213外洩出，以減低泵流量，達到迅速調降油壓 的效果。而且，相較於一般將釋壓閥設置在齒輪式油泵的 出口與主油道間的方式，因持續、固定的泵流量會造成後 端或壓緩慢’又釋壓閥因必須長時間維持開啟狀態而壽命籲 較短，该洩壓閥25則是利用改變泵流量以能控制油壓迅速 降至正常，不需長時間開啟，使用壽命相對增長。 綜上所述，本發明的齒輪式油泵2，利用該洩壓閥25 能改變泵流量的設計，整體產生迅速調降油壓與節能省電 等功效，所以確實能達成本發明的目的。 惟以上所述者，僅為本發明之較佳實施例而已，當不The anti-deformation force drives the valve plug 253 to automatically shift to the left to stop the oil suction chamber 211 from continuing to drain. As shown in FIG. 5, the relationship between the gear rotation speed and the pump flow rate when the disc-type oil pump 2 is subjected to the characteristic test is as follows: the engine oil of the type 1 is 40 is selected, and the maximum oil temperature value is controlled at 125t, and The maximum oil pressure ^ is controlled in the bars. In theory, the millet flow (or oil pressure) is linear with the gear speed: (see the imaginary line in Figure 5), and the gear speed is twice the engine speed 'so' as the gear speed increases, the pump flow (or oil pressure) may be too large to exceed the system limit and actual demand; and the test results can be inferred that when the gear speed is between uoo~2〇00 rev/min (rev/min), _ is in accordance with the system limit and At this time, the (four) valve 25 does not act, that is, the oil suction chamber, so the pump flow at this stage is slightly linear with the gear speed; and when the gear speed is greater than 2 rev / min, the pump flow The valve 25 has been activated to start the operation of the oil in the oil suction chamber 2U through the oil drain 213. Therefore, it is apparent from the figure that the increase in the pump flow rate with the increase of the gear speed has been slowed down. At this time, the output fruit flow can still meet the system requirements. Similarly, the gear type 201107604 has a similar characteristic curve between the gear speed and the oil pressure. Therefore, with the design of the pressure relief valve 25, when the oil pressure and the flow of the oil discharge chamber 212 are excessively large, the excess oil moves the valve plug 253 to make the switch hole 256 communicate with the oil drain hole 257, so that The oil in the oil suction chamber 211 is discharged from the oil drain 213 to reduce the pump flow rate and achieve the effect of rapidly reducing the oil pressure. Moreover, compared with the way in which the pressure relief valve is generally disposed between the outlet of the gear oil pump and the main oil passage, the continuous or fixed pump flow rate causes the rear end or the pressure to be slow and the pressure relief valve must remain open for a long time. The state and the life expectancy is short. The pressure relief valve 25 uses the change of the pump flow rate to control the oil pressure to quickly drop to normal, and does not need to be opened for a long time, and the service life is relatively increased. In summary, the gear type oil pump 2 of the present invention can change the design of the pump flow rate by using the pressure relief valve 25, and the overall effect of rapidly reducing the oil pressure and energy saving, so that the object of the present invention can be achieved. However, the above is only the preferred embodiment of the present invention, when not
屬本發明專利涵蓋之範圍内。 【圖式簡單說明】It is within the scope of the patent of the present invention. [Simple description of the map]
施例的結構；Structure of the example;
、一泡油道、一排油腔，與一 孔與一洩油孔的相對位置關係； ，說明該較佳實施例之一吸油腔 與一洩壓閥之一開關孔、一旁通 10 201107604 圖3是一剖視示意圖，說明該較佳實施例之該洩壓閥 的一閥塞是處於一非泡油位置； 圖4是一剖視示意圖，說明該較佳實施例之該洩壓閥 之閥塞是處於一洩油位置；以及 圖5是一曲線圖，說明該較佳實施例之齒輪轉速與泵 流量的關係。a foaming oil passage, a row of oil chambers, and a relative positional relationship between a hole and a drain hole; and illustrating one of the oil suction chamber and a pressure relief valve of the preferred embodiment, a bypass hole, a bypass 10 201107604 3 is a schematic cross-sectional view showing a valve plug of the pressure relief valve of the preferred embodiment in a non-foaming position; FIG. 4 is a cross-sectional view showing the pressure relief valve of the preferred embodiment. The valve plug is in a drain position; and Figure 5 is a graph illustrating the relationship between the gear speed of the preferred embodiment and the pump flow.
11 201107604 【主要元件符號說明】 2 齒 輪式油泵 25 洩壓閥 21 泵 殼 251 座體 210 輸 油空間 252 栓塞 211 吸 油腔 253 閥塞 212 排 油腔 254 彈性件 213 洩 油道 255 旁通孔 22 泵 蓋 256 開關孔 221 進 油口 257 洩油孔 222 出 油口 258 第一均徑端部 23 齒輪 259 第二均徑端部 231 齒 縫 250 縮徑部 24 齒 輪 261 左端 241 齒 縫 262 右端 271 左端 272 右端 1211 201107604 [Description of main components] 2 Gear oil pump 25 Pressure relief valve 21 Pump housing 251 Seat 210 Oil delivery space 252 Plug 211 Oil suction chamber 253 Valve plug 212 Oil drain chamber 254 Elastic member 213 Oil drain 255 Bypass hole 22 Pump cover 256 Switch hole 221 Inlet port 257 Drain hole 222 Outlet port 258 First mean diameter end 23 Gear 259 Second equal diameter end 231 Tooth gap 250 Reduced diameter 24 Gear 261 Left end 241 Tooth 262 Right end 271 Left end 272 right end 12